Scroll compressor

Abstract

The present application provides a scroll compressor which improves durability of the scroll compressor while suppressing the number of components. In a case where a bushing moves in an axial direction of a rotation shaft toward a revolving scroll (26) between a top end of the rotation shaft and the revolving scroll (26), a bushing flange portion comes into abutment with a bearing flange portion (58). A groove (61) which extends in a manner to supply oil from a supply passage (46) toward the bearing flange portion (58) is formed in the bearing cylinder portion (57). Therefore, oil from the supply passage (46) is easily supplied to the bearing flange portion (58) via the groove (61). An indentation (62) which communicates with the groove (61) and supplies oil toward an outer periphery of the bearing flange portion (58) is formed in the bearing flange portion (58). Therefore, oil supplied from the groove (61) to the bearing flange portion (58) is easily supplied to the outer periphery of the bearing flange portion (58) via the indentation (62).

Description

Technical Field

[0001] This invention relates to scroll compressors. Background Technology

[0002] A scroll compressor comprises a housing, a rotating shaft, and a compression mechanism. The housing has a suction inlet and a discharge outlet. Refrigerant is drawn in through the suction inlet and discharged through the discharge outlet. The rotating shaft is housed within the housing. The rotating shaft is rotatably supported by the housing. An eccentric shaft is provided on the rotating shaft. The eccentric shaft protrudes from the top of the rotating shaft. The eccentric shaft extends parallel to the rotating shaft at a position eccentric to its central axis.

[0003] The compression mechanism has a fixed scroll member and a rotating scroll member. The fixed scroll member is fixed to the housing. The fixed scroll member has a fixed base plate, a fixed scroll wall, and a fixed outer peripheral wall. The fixed scroll wall stands upright from the fixed base plate. The fixed outer peripheral wall stands upright from the fixed base plate and surrounds the fixed scroll wall. The rotating scroll member revolves by the rotation of a rotation axis. The rotating scroll member has a rotating base plate and a rotating scroll wall. The rotating base plate faces the fixed base plate. The rotating scroll wall stands upright from the rotating base plate toward the fixed base plate and revolves inside the fixed outer peripheral wall.

[0004] A compression chamber is formed in the compression mechanism. The compression chamber is divided by a fixed base plate, a fixed vortex wall, a rotating base plate, and a rotating vortex wall. The compression chamber compresses the drawn-in refrigerant by the meshing of the fixed vortex wall and the rotating vortex wall.

[0005] The housing includes a shaft support housing. The shaft support housing is positioned on the side opposite to the fixed substrate relative to the gyratory substrate. The shaft support housing supports the rotation shaft. A back pressure chamber is formed between the end face of the gyratory substrate on the side opposite to the fixed substrate (i.e., the substrate end face) and the shaft support housing. Refrigerant for applying force to the gyratory substrate towards the fixed substrate is introduced into the back pressure chamber. An oil supply hole is formed in the gyratory scroll member. The oil supply hole opens toward the back pressure chamber, supplying oil to the back pressure chamber.

[0006] An eccentric shaft is inserted into the bushing. The bushing can swing around the eccentric shaft. A bottomed cylindrical recess is formed on the end face of the substrate. The bushing is disposed in the recess. An oil supply hole opens on the bottom surface dividing the recess.

[0007] For example, as disclosed in Patent Document 1, a sliding bearing is disposed on the inner circumferential surface of the recess. The sliding bearing supports the bushing so that it can rotate. The bushing has a cylindrical bushing portion disposed inside the sliding bearing. The sliding bearing has a bearing sleeve portion disposed on the inner circumferential surface of the recess.

[0008] Existing technical documents

[0009] Patent documents

[0010] Patent Document 1: Japanese Patent Application Publication No. 2014-173436 Summary of the Invention

[0011] The problem that the invention aims to solve

[0012] In such scroll compressors, the bushing sometimes moves axially toward the scroll member between the top of the rotating shaft and the scroll member. When the bushing moves axially toward the scroll member, it may come into contact with the scroll member. This contact causes wear between the bushing and the scroll member, thus degrading the durability of the scroll compressor.

[0013] Therefore, for example, it is considered to provide additional components to limit the axial movement of the bushing toward the cycloidal scroll member on the rotating shaft, or to provide additional components with high wear resistance, different from the sliding bearing, between the bushing and the cycloidal scroll member on the rotating shaft. However, this increases the number of components, which is not preferable. Therefore, it is desirable to improve the durability of the scroll compressor while reducing the number of components.

[0014] Methods for solving problems

[0015] A scroll compressor that solves the above-mentioned problems includes: a housing having a refrigerant inlet and a refrigerant outlet; a rotating shaft housed within the housing and rotatably supported thereon; and a compression mechanism having a fixed scroll member fixed to the housing and a revolving scroll member revolving by the rotation of the rotating shaft. An eccentric shaft is provided on the rotating shaft, protruding from its top end and extending parallel to the rotating shaft at a position eccentric to its central axis. The fixed scroll member has a fixed base plate and a fixed scroll wall erected from the fixed base plate. The rotary vortex member has a fixed outer peripheral wall that stands upright from the fixed base plate and surrounds the fixed vortex wall. It has a rotary base plate facing the fixed base plate and a rotary vortex wall that stands upright from the rotary base plate toward the fixed base plate and revolves inside the fixed outer peripheral wall. The compression mechanism has a compression chamber formed by the fixed base plate, the fixed vortex wall, the rotary base plate, and the rotary vortex wall, which compresses the drawn-in refrigerant through the engagement of the fixed vortex wall and the rotary vortex wall. The housing has a rotating shaft positioned opposite the fixed base plate. A shaft support housing has a back pressure chamber formed between the end face of the rotating substrate opposite to the fixed substrate (i.e., the substrate end face) and the shaft support housing. This chamber allows for the introduction of refrigerant to exert force on the rotating substrate towards the fixed substrate. An oil supply hole is formed in the rotating scroll member, opening towards the back pressure chamber and supplying oil to it. A bushing capable of oscillating around the eccentric shaft is inserted into the eccentric shaft. A bottomed cylindrical recess is formed on the substrate end face, housing the bushing. A sliding bearing supporting the bushing for rotation is disposed on the inner circumferential surface dividing the recess. The oil supply hole is located on the bottom surface dividing the recess. The bushing has a bushing sleeve portion disposed inside the sliding bearing, and the sliding bearing has a bearing sleeve portion disposed on the inner circumferential surface. The bushing has a bushing flange portion that protrudes radially outward from the bushing sleeve portion toward the rotating shaft. The sliding bearing has a bearing flange portion that protrudes radially outward from the bearing sleeve portion and is disposed between the end face of the substrate and the bushing flange portion. A groove is formed in the bearing sleeve portion to supply oil from the oil supply hole toward the bearing flange portion. A notch is formed in the bearing flange portion that communicates with the groove and supplies oil toward the outer periphery of the bearing flange portion.

[0016] Therefore, even if the bushing moves axially toward the vortex member between the top of the rotating shaft and the vortex member, the bushing flange abuts against the bearing flange. Thus, even if the bushing moves axially toward the vortex member between the top of the rotating shaft and the vortex member, contact between the bushing and the vortex member can be avoided. Therefore, problems such as wear between the vortex member and bushing caused by contact between the bushing and the vortex member can be avoided. Therefore, for example, it is unnecessary to provide additional components to limit the axial movement of the bushing toward the vortex member, or to provide additional components with high wear resistance, different from those of a sliding bearing, between the bushing and the vortex member along the axial direction of the rotating shaft.

[0017] Furthermore, a groove extending from the oil supply hole toward the bearing flange is formed in the bearing housing. Therefore, oil from the oil supply hole is easily supplied to the bearing flange via the groove. Additionally, a notch communicating with the groove and supplying oil toward the outer periphery of the bearing flange is formed in the bearing flange. Therefore, oil supplied from the groove to the bearing flange is easily supplied to the outer periphery of the bearing flange via the notch. As a result, even when the bushing flange and bearing flange abut against each other, good lubrication between the bearing flange and bushing flange is achieved. Through these methods, the durability of the scroll compressor can be improved while reducing the number of components.

[0018] In the above-described scroll compressor, preferably, when viewed axially along the rotation axis, if the straight line connecting the center of the recess and the oil supply hole is designated as the first straight line, and the straight line passing through the center of the recess and extending in a direction orthogonal to the first straight line is designated as the second straight line, then the oil supply hole opens at a portion of the bottom surface across the second straight line on the side opposite to the groove.

[0019] This allows the distance from the oil supply hole to the groove to be as far as possible, thus facilitating the supply of oil from the oil supply hole to the inner circumferential surface of the bearing housing. Consequently, good lubrication between the bearing housing and the bushing housing is achieved. Therefore, the durability of the scroll compressor can be further improved.

[0020] In the above-described scroll compressor, preferably, the bearing flange abuts against the end face of the base plate to press the swirling scroll toward the fixed scroll, and abuts against the bushing flange to press the bushing toward the top of the rotating shaft.

[0021] This allows the bushing to be positioned axially on the rotating shaft. Consequently, axial movement of the bushing between the top of the rotating shaft and the gyratory scroll member can be suppressed.

[0022] In the aforementioned scroll compressor, it is preferable that the bearing flange portion has: a first extension that extends in an arc shape from the bearing cylinder portion toward the radially outward side and abuts against the bushing flange portion; and a second extension that extends in an arc shape obliquely toward the substrate end face from the end of the first extension on the side opposite to the bearing cylinder portion and abuts against the substrate end face. This configuration is suitable for positioning the bushing axially on the rotating shaft.

[0023] In the aforementioned scroll compressor, it is preferable that the bearing flange portion has: a first extension portion that extends in an arc shape from the bearing cylinder portion toward the radially outward side and abuts against the end face of the base plate; and a second extension portion that extends in an arc shape obliquely toward the bushing flange portion from the end of the first extension portion on the side opposite to the bearing cylinder portion and abuts against the bushing flange portion. This configuration is suitable for positioning the bushing axially on the rotating shaft.

[0024] Invention Effects

[0025] According to the present invention, the durability of a scroll compressor can be improved while reducing the number of components. Attached Figure Description

[0026] Figure 1 This is a cross-sectional view of the scroll compressor of the embodiment.

[0027] Figure 2 It is a cross-sectional view showing an enlarged portion of a scroll compressor.

[0028] Figure 3 It is a three-dimensional diagram showing a gyratory scroll component and a sliding bearing.

[0029] Figure 4 It is a three-dimensional diagram showing the gyratory scroll component and the sliding bearing.

[0030] Figure 5 This is a front view showing the gyratory scroll and the sliding bearing.

[0031] Figure 6 This is an enlarged cross-sectional view showing a portion of the modified scroll compressor.

[0032] Explanation of reference numerals in the attached figures

[0033] 10…Scroll compressor, 11…Housing, 12h…Inlet, 13…Shaft support housing, 14h…Outlet, 15…Rotating shaft, 15e…Top, 25…Fixed scroll component, 25a…Fixed base plate, 25b…Fixed scroll wall, 25c…Fixed outer peripheral wall, 26…Rotating scroll component, 26a…Rotating base plate, 26b…Rotating scroll wall, 26f…Base plate end face, 27…Compression chamber, 45…Back pressure chamber, 46…Air supply passage functioning as an oil supply port, 47…Recess, 47a…Bottom surface, 47b…Inner peripheral surface, 50…Eccentric shaft, 51…Bushing, 52…Bushing sleeve portion, 53…Bushing flange portion, 56…Sliding bearing, 57…Bearing sleeve portion, 58…Bearing flange portion, 59…First extension, 60…Second extension, 61…Groove, 62…Notch, C1…Compression mechanism. Detailed Implementation

[0034] The following is based on Figures 1-5 An embodiment of a scroll compressor will be described. This scroll compressor is used, for example, in a vehicle air conditioning system.

[0035] <Basic Components of a Scroll Compressor>

[0036] like Figure 1 As shown, the scroll compressor 10 includes a cylindrical housing 11. The housing 11 includes a motor housing 12, a shaft support housing 13, and a discharge housing 14. The motor housing 12, shaft support housing 13, and discharge housing 14 are made of metal, for example, aluminum. Furthermore, the scroll compressor 10 includes a rotating shaft 15. The rotating shaft 15 is housed within the housing 11.

[0037] The motor housing 12 has a plate-shaped end wall 12a and a cylindrical peripheral wall 12b. The peripheral wall 12b extends cylindrically from the outer periphery of the end wall 12a. The axial direction of the peripheral wall 12b is aligned with the axial direction of the rotating shaft 15. The motor housing 12 has a plurality of internally threaded holes 12c. Each internally threaded hole 12c is formed at the open end of the peripheral wall 12b. Furthermore, in Figure 1 For ease of explanation, only one internal threaded hole 12c is shown in the diagram. Additionally, the motor housing 12 has a suction port 12h. Therefore, the housing 11 has a suction port 12h. The suction port 12h draws in refrigerant. The suction port 12h is formed in the portion of the peripheral wall 12b located on the end wall 12a side. The suction port 12h connects the inside and outside of the motor housing 12.

[0038] The motor housing 12 has a cylindrical bearing retainer 12d. The bearing retainer 12d protrudes from the center of the inner surface of the end wall 12a. One axial end of the rotating shaft 15, i.e., the first end, is inserted into the bearing retainer 12d. The scroll compressor 10 includes a bearing 16. The bearing 16 is, for example, a rolling bearing. The bearing 16 is disposed between the inner circumferential surface of the bearing retainer 12d and the outer circumferential surface of the first end of the rotating shaft 15. Furthermore, the first end of the rotating shaft 15 is rotatably supported on the motor housing 12 via the bearing 16.

[0039] The shaft support housing 13 has a plate-shaped end wall 17 and a cylindrical peripheral wall 18. The peripheral wall 18 extends cylindrically from the outer periphery of the end wall 17. The axial direction of the peripheral wall 18 is aligned with the axial direction of the rotating shaft 15. In addition, the shaft support housing 13 has an annular flange wall 19. The flange wall 19 extends radially outward from the end of the outer peripheral surface of the peripheral wall 18 on the side opposite to the end wall 17 toward the rotating shaft 15.

[0040] The shaft support housing 13 has a circular through hole 17a. The through hole 17a is formed in the center of the end wall 17. The through hole 17a extends through the end wall 17 in the thickness direction. A rotating shaft 15 is inserted into the through hole 17a. The top end 15e of the second end side, located on the other side of the axial direction of the rotating shaft 15, is located inside the peripheral wall 18.

[0041] The scroll compressor 10 includes a bearing 21. The bearing 21 is, for example, a rolling bearing. The bearing 21 is disposed between the inner circumferential surface of the peripheral wall 18 and the outer circumferential surface of the rotating shaft 15. Furthermore, the rotating shaft 15 is rotatably supported on the shaft support housing 13 via the bearing 21. Therefore, the shaft support housing 13 supports the rotating shaft 15 so that it can rotate. In this way, the rotating shaft 15 is rotatably supported on the housing 11.

[0042] The shaft support housing 13 has a plurality of bolt insertion holes 19a. Each bolt insertion hole 19a is formed on the outer periphery of the flange wall 19. Each bolt insertion hole 19a penetrates the flange wall 19 in the thickness direction. Each bolt insertion hole 19a of the flange wall 19 communicates with each internal threaded hole 12c of the motor housing 12. Furthermore, in Figure 1 For ease of explanation, only one bolt insertion hole 19a is shown in the figure.

[0043] The scroll compressor 10 includes a motor chamber 20. The motor chamber 20 is defined by a motor housing 12 and a shaft support housing 13. The motor housing 12 and the shaft support housing 13 together define the motor chamber 20. Thus, the motor chamber 20 is formed within the housing 11. The motor chamber 20 communicates with the suction inlet 12h. Refrigerant from the suction inlet 12h is drawn into the motor chamber 20. Therefore, the motor chamber 20 is the suction pressure region.

[0044] 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 rotating shaft 15. The stator 23 surrounds the rotor 24. The rotor 24 has a rotor core 24a fixed to the rotating shaft 15 and a plurality of permanent magnets (not shown) disposed on the rotor core 24a.

[0045] The stator 23 has a cylindrical stator core 23a and a motor coil 23b. The stator core 23a is fixed to the inner circumferential surface of the peripheral wall 12b of the motor housing 12. The motor coil 23b is wound around the stator core 23a. The rotor 24 rotates by supplying power controlled by an inverter (not shown) to the motor coil 23b. Consequently, the rotating shaft 15 rotates integrally with the rotor 24. Therefore, the motor 22 causes the rotating shaft 15 to rotate.

[0046] The scroll compressor 10 includes a compression mechanism C1. The compression mechanism C1 has a fixed scroll member 25 and a rotary scroll member 26. Therefore, the scroll compressor 10 includes a fixed scroll member 25 and a rotary scroll member 26. The compression mechanism C1 is scroll type. The rotary scroll member 26 revolves relative to the fixed scroll member 25 by the rotation of the rotating shaft 15.

[0047] The fixed vortex member 25 has a fixed base plate 25a, a fixed vortex wall 25b, and a fixed outer peripheral wall 25c. The fixed base plate 25a is circular. A discharge port 25h is formed in the center of the fixed base plate 25a. The discharge port 25h is circular. The discharge port 25h penetrates the fixed base plate 25a in the thickness direction. The fixed vortex wall 25b rises from the fixed base plate 25a. The fixed outer peripheral wall 25c rises from the outer periphery of the fixed base plate 25a. The fixed outer peripheral wall 25c surrounds the fixed vortex wall 25b.

[0048] The scroll compressor 10 includes a valve mechanism 25v. The valve mechanism 25v is mounted on the side of the fixed base plate 25a opposite to the fixed scroll wall 25b. The valve mechanism 25v is configured to open and close the discharge port 25h.

[0049] The gyratory scroll member 26 has a gyratory base plate 26a and a gyratory scroll wall 26b. The gyratory base plate 26a is circular. The gyratory base plate 26a faces the fixed base plate 25a. The gyratory scroll wall 26b rises from the gyratory base plate 26a toward the fixed base plate 25a. The gyratory scroll wall 26b engages with the fixed scroll wall 25b. The gyratory scroll member 26 is located inside the fixed outer peripheral wall 25c. The gyratory scroll member 26 revolves inside the fixed outer peripheral wall 25c. Therefore, the gyratory scroll wall 26b revolves inside the fixed outer peripheral wall 25c. The top surface of the fixed scroll wall 25b contacts the gyratory base plate 26a. The top surface of the gyratory scroll wall 26b contacts the fixed base plate 25a.

[0050] A compression chamber 27 is formed in the compression mechanism C1. The compression chamber 27 is divided by a fixed base plate 25a, a fixed scroll wall 25b, a rotating base plate 26a, and a rotating scroll wall 26b. Therefore, the compression chamber 27 is formed between the fixed scroll member 25 and the rotating scroll member 26. The compression chamber 27 compresses the intake refrigerant by the engagement of the fixed scroll wall 25b and the rotating scroll wall 26b.

[0051] The rotary substrate 26a has a protrusion 28. The protrusion 28 protrudes from a first surface 26e of the rotary substrate 26a located on the side opposite to the fixed substrate 25a. The protrusion 28 protrudes from the center of the first surface 26e toward the shaft support housing 13. The shaft support housing 13 is disposed on the side opposite to the fixed substrate 25a relative to the rotary substrate 26a. The axial direction of the protrusion 28 is aligned with the axial direction of the rotation shaft 15. The first surface 26e and the top surface 28a of the protrusion 28 form the end face of the rotary substrate 26a on the side opposite to the fixed substrate 25a, namely the substrate end face 26f. Furthermore, the inner side of the protrusion 28 is a recess 47 formed on the substrate end face 26f. Therefore, a bottomed cylindrical recess 47 is formed on the substrate end face 26f.

[0052] The rotary substrate 26a has a plurality of grooves 26d. The plurality of grooves 26d are respectively formed around the protrusions 28 in the first surface 26e of the rotary substrate 26a. The plurality of grooves 26d are arranged at predetermined intervals in the circumferential direction of the rotation axis 15. Furthermore, in Figure 1 For ease of explanation, only one groove 26d is shown in the figure. A circular 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 of the vortex member 26 in the shaft support housing 13.

[0053] The scroll compressor 10 includes an elastic plate 31. The elastic plate 31 is annular. The elastic plate 31 is clamped between the end face 13e of the shaft support housing 13 and the open end face of the fixed outer peripheral wall 25c. Furthermore, the elastic plate 31 always exerts a force on the rotating scroll member 26 toward the fixed scroll member 25.

[0054] The discharge housing 14 has a plate-shaped end wall 14a and a cylindrical peripheral wall 14b. The peripheral wall 14b extends cylindrically from the outer periphery of the end wall 14a. The axial direction of the peripheral wall 14b is aligned with the axial direction of the rotation shaft 15. The peripheral wall 14b surrounds the fixed scroll member 25. Therefore, the fixed scroll member 25 is housed within the housing 11.

[0055] The discharge housing 14 has a plurality of bolt insertion holes 14c. Each bolt insertion hole 14c is formed in the peripheral wall 14b. Furthermore, in Figure 1For ease of explanation, only one bolt insertion hole 14c is shown in the figure. Each bolt insertion hole 14c communicates with each bolt insertion hole 19a of the flange wall 19.

[0056] Bolts B1, through the bolt holes 14c, are screwed into the internal threaded holes 12c of the motor housing 12 via the bolt holes 19a of the flange wall 19 (threaded engagement). Thus, the shaft support housing 13 is connected to the peripheral wall 12b of the motor housing 12, and the discharge housing 14 is connected to the flange wall 19 of the shaft support housing 13. Therefore, the motor housing 12, shaft support housing 13, and discharge housing 14 are arranged sequentially along the axial direction of the rotating shaft 15 in this order. The fixed scroll member 25 is clamped between the end wall 14a of the discharge housing 14 and the shaft support housing 13. In this way, the fixed scroll member 25 is fixed to the housing 11.

[0057] The scroll compressor 10 includes a suction passage 35. The suction passage 35 has a first groove 36, a first hole 37, a second groove 38, and a second hole 39. The first groove 36 is formed on a portion of the inner circumferential surface of the peripheral wall 12b of the motor housing 12. The first groove 36 opens at the open end of the peripheral wall 12b. The first hole 37 is formed on the outer circumferential portion of the flange wall 19 of the shaft support housing 13. The first hole 37 penetrates the flange wall 19 in the thickness direction. The first hole 37 communicates with the first groove 36. The second groove 38 is formed on a portion of the inner circumferential surface of the peripheral wall 14b of the discharge housing 14. The second groove 38 communicates with the first hole 37. The second hole 39 is formed on the fixed outer circumferential wall 25c of the fixed scroll member 25. The second hole 39 penetrates the fixed outer circumferential wall 25c in the thickness direction. The second hole 39 communicates with the second groove 38. The second hole 39 communicates with the outermost circumferential portion of the compression chamber 27.

[0058] The refrigerant in the motor chamber 20 is drawn into the compression chamber 27 through the first slot 36, the first hole 37, the second slot 38, and the second hole 39. The refrigerant drawn into the compression chamber 27 is compressed within the compression chamber 27 by the revolution of the vortex member 26. In this way, the compression mechanism C1 compresses the refrigerant drawn into the housing 11.

[0059] The scroll compressor 10 includes a discharge chamber 40. The discharge chamber 40 is divided between the fixed base plate 25a and the end wall 14a of the discharge housing 14. The discharge chamber 40 communicates with the discharge port 25h. Refrigerant compressed in the compression chamber 27 is discharged into the discharge chamber 40. The discharge housing 14 has a discharge outlet 14h. Therefore, the housing 11 has a discharge outlet 14h. The discharge outlet 14h is formed in the end wall 14a of the discharge housing 14. The discharge outlet 14h communicates with the discharge chamber 40. The discharge outlet 14h discharges the refrigerant from the discharge chamber 40 to the outside.

[0060] A back pressure chamber 45 is defined between the rotating base plate 26a of the gyratory scroll member 26 and the shaft support housing 13. The back pressure chamber 45 is formed within the housing 11 on the side opposite to the fixed base plate 25a, relative to the rotating base plate 26a. Thus, a back pressure chamber 45 is formed between the base plate end face 26f and the shaft support housing 13. The shaft support housing 13 separates the back pressure chamber 45 from the motor chamber 20. The inner side of the peripheral wall 18 of the shaft support housing 13 is part of the back pressure chamber 45. Furthermore, the gap between the elastic plate 31 and the shaft support housing 13 is part of the back pressure chamber 45.

[0061] The scroll compressor 10 includes an air supply passage 46. The air supply passage 46 is formed in the scroll member 26. A first end of the air supply passage 46 opens at the top end of the scroll wall 26b. This first end of the air supply passage 46 communicates with the compression chamber 27. A second end of the air supply passage 46 opens at the bottom surface 47a of the dividing recess 47. This second end of the air supply passage 46 communicates with the back pressure chamber 45. The air supply passage 46 extends through the inner end of the scroll wall 26b, which converges in a scroll shape towards the center of the scroll member 26, and the scroll base plate 26a. The air supply passage 46 is a through-hole in the shape of a circular aperture.

[0062] Furthermore, the gas supply passage 46 supplies a portion of the refrigerant compressed in the compression chamber 27 to the back pressure chamber 45. As a result, the pressure in the back pressure chamber 45 is higher than that in the motor chamber 20. By increasing the pressure in the back pressure chamber 45, force is applied to the gyratory platen 26a toward the fixed platen 25a such that the top tip of the gyratory vortex wall 26b presses against the fixed platen 25a. In this way, refrigerant is introduced into the back pressure chamber 45 to apply force to the gyratory platen 26a toward the fixed platen 25a.

[0063] Furthermore, the gas supply passage 46 supplies oil contained in the refrigerant to the back pressure chamber 45 along with the refrigerant. Therefore, the gas supply passage 46 also functions as an oil supply orifice for supplying oil to the back pressure chamber 45. Thus, an oil supply orifice is formed in the vortex member 26 that opens toward the back pressure chamber 45 and supplies oil to the back pressure chamber 45. Moreover, the gas supply passage 46, which serves as an oil supply orifice, opens at the bottom surface 47a of the dividing recess 47.

[0064] An eccentric shaft 50 is provided on the rotating shaft 15. The eccentric shaft 50 protrudes from the top end 15e of the rotating shaft 15 and extends parallel to the rotating shaft 15 at an eccentric position relative to the central axis L1 of the rotating shaft 15. The eccentric shaft 50 is integrally formed with the rotating shaft 15. The axial direction of the eccentric shaft 50 is aligned with the axial direction of the rotating shaft 15. The eccentric shaft 50 protrudes from the top end 15e of the rotating shaft 15 toward the vortex member 26. The eccentric shaft 50 is inserted into the recess 47.

[0065] Liner

[0066] like Figure 2As shown, an eccentric shaft 50 is inserted into a bushing 51. The bushing 51 has a bushing sleeve portion 52 and a bushing flange portion 53. The eccentric shaft 50 is inserted into the inner side of the bushing sleeve portion 52. The bushing sleeve portion 52 is disposed inside the recess 47. Therefore, the bushing 51 is disposed in the recess 47.

[0067] The end of the bushing sleeve portion 52 opposite to the rotating base plate 26a protrudes from the protrusion 28. The bushing flange portion 53 protrudes outward in an annular shape from the end of the bushing sleeve portion 52 opposite to the rotating base plate 26a. The bushing flange portion 53 protrudes radially outward from the bushing sleeve portion 52 towards the rotation axis 15. The bushing flange portion 53 overlaps with the top surface 28a of the protrusion 28 in the axial direction of the protrusion 28. The bushing 51 is capable of swinging about the eccentric axis 50.

[0068] The scroll compressor 10 includes a counterweight 55. The counterweight 55 is integrally formed with the bushing 51. The counterweight 55 protrudes outward from a portion of the outer peripheral surface of the bushing flange 53. The counterweight 55 is housed within the peripheral wall 18 of the shaft support housing 13.

[0069] <Sliding bearing>

[0070] A sliding bearing 56 is disposed on the inner circumferential surface 47b of the recess 47. The sliding bearing 56 is cylindrical. The sliding bearing 56 is formed by bending a strip of metal into an arc shape. Therefore, the sliding bearing 56 is non-annular.

[0071] The sliding bearing 56 has a bearing sleeve portion 57 and a bearing flange portion 58. The bearing sleeve portion 57 is disposed on the inner peripheral surface 47b of the recess 47. The bearing sleeve portion 57 is disposed between the inner peripheral surface 47b of the recess 47 and the outer peripheral surface of the bushing sleeve portion 52. The bushing sleeve portion 52 is disposed inside the sliding bearing 56. The sliding bearing 56 supports the bushing 51 so that it can rotate.

[0072] The end portion of the bearing sleeve portion 57 opposite to the rotating base plate 26a protrudes from the recess 47. The bearing flange portion 58 protrudes outward in an annular shape from the end portion of the bearing sleeve portion 57 opposite to the rotating base plate 26a. The bearing flange portion 58 protrudes radially outward from the bearing sleeve portion 57 towards the rotation shaft 15. The bearing flange portion 58 is disposed between the top surface 28a of the protrusion 28 and the bushing flange portion 53. Therefore, the bearing flange portion 58 is disposed between the base plate end face 26f and the bushing flange portion 53.

[0073] The bearing flange portion 58 has a first extension portion 59 and a second extension portion 60. The first extension portion 59 extends in an arc shape from the bearing sleeve portion 57 toward the radially outer side of the rotating shaft 15. The first extension portion 59 extends along the bushing flange portion 53. The first extension portion 59 abuts against the bushing flange portion 53. The second extension portion 60 extends in an arc shape obliquely toward the substrate end face 26f from the end of the first extension portion 59 on the side opposite to the bearing sleeve portion 57. The second extension portion 60 abuts against the top surface 28a of the protrusion portion 28. Therefore, the second extension portion 60 abuts against the substrate end face 26f. Furthermore, the bearing flange portion 58 abuts against the substrate end face 26f to press the swirling scroll member 26 toward the fixed scroll member 25, and abuts against the bushing flange portion 53 to press the bushing 51 toward the top surface 15e of the rotating shaft 15.

[0074] The rotation of the rotating shaft 15 is transmitted to the gyratory scroll member 26 via the eccentric shaft 50, bushing 51, and sliding bearing 56. This causes the gyratory scroll member 26 to rotate. Furthermore, the rotation of the gyratory scroll member 26 is prevented by the contact between each pin 30 and the inner circumferential surface of each ring member 29, allowing only its revolution. Thus, the gyratory scroll member 26 revolves with its gyratory scroll wall 26b in contact with the fixed scroll wall 25b. As the gyratory scroll member 26 revolves, the volume of the compression chamber 27 decreases, thereby compressing the refrigerant within the compression chamber 27. The gyratory scroll member 26 revolves inside the fixed outer circumferential wall 25c as the rotating shaft 15 rotates. The counterweight 55 counteracts the centrifugal force acting on the gyratory scroll member 26 during its revolution. This reduces the imbalance of the gyratory scroll member 26.

[0075] <groove>

[0076] like Figure 3 and Figure 4 As shown, a groove 61 is formed in the bearing sleeve portion 57. The groove 61 is formed between a first edge 571 located on one side of the bearing sleeve portion 57 in the circumferential direction and a second edge 572 located on the other side of the bearing sleeve portion 57 in the circumferential direction. The groove 61 is the gap between the first edge 571 and the second edge 572. The groove 61 extends from the first end edge of the bearing sleeve portion 57 in the axial direction to the second end edge. The groove 61 extends in a manner that supplies oil from the air supply passage 46 toward the bearing flange portion 58.

[0077] like Figure 5 As shown, when viewed along the axial direction of the rotation axis 15, the straight line connecting the center P10 of the recess 47 and the air supply passage 46 is designated as the first straight line L11. Furthermore, the straight line passing through the center P10 of the recess 47 and extending in a direction orthogonal to the first straight line L11 is designated as the second straight line L12. Thus, the air supply passage 46 opens in the bottom surface 47a at a location opposite to the groove 61, across the second straight line L12.

[0078] <Gap>

[0079] A notch 62 is formed in the bearing flange portion 58. The notch 62 is formed by a first notch edge 621 and a second notch edge 622. The first notch edge 621 is continuous with the first edge 571. The second notch edge 622 is continuous with the second edge 572. Therefore, the notch 62 communicates with the groove 61. The first notch edge 621 connects the first edge 571 to the outer periphery of the bearing flange portion 58. The second notch edge 622 connects the second edge 572 to the outer periphery of the bearing flange portion 58. The first notch edge 621 and the second notch edge 622 extend in a direction separating from each other as they leave the groove 61. When viewed axially along the rotation axis 15, the notch 62 is cut out at an obtuse angle between the first notch edge 621 and the second notch edge 622. When viewed axially along the rotation axis 15, the notch 62 is cut out from the first extension portion 59 to the second extension portion 60. Oil is supplied to the outer periphery of the bearing flange 58 through the notch 62.

[0080] [The Role of the Implementation Method]

[0081] Next, the function of the implementation method will be explained.

[0082] In this scroll compressor 10, the bushing 51 sometimes moves axially toward the scroll member 26 between the top end 15e of the rotating shaft 15 and the scroll member 26. When the bushing 51 moves axially toward the scroll member 26 between the top end 15e of the rotating shaft 15 and the scroll member 26, the bushing flange 53 abuts against the bearing flange 58. Therefore, even if the bushing 51 moves axially toward the scroll member 26 between the top end 15e of the rotating shaft 15 and the scroll member 26, it is possible to avoid contact between the bushing 51 and the scroll member 26. Thus, the problem of wear between the scroll member 26 and the bushing 51 due to contact between the bushing 51 and the scroll member 26 is avoided.

[0083] A groove 61 is formed in the bearing housing portion 57, extending towards the bearing flange portion 58 from the air supply passage 46. Therefore, oil from the air supply passage 46 can be easily supplied to the bearing flange portion 58 via the groove 61. Furthermore, a notch 62 is formed in the bearing flange portion 58, communicating with the groove 61 and supplying oil towards the outer periphery of the bearing flange portion 58. Therefore, oil supplied from the groove 61 to the bearing flange portion 58 can be easily supplied to the outer periphery of the bearing flange portion 58 via the notch 62. As a result, even when the bushing flange portion 53 abuts against the bearing flange portion 58, lubrication between the bearing flange portion 58 and the bushing flange portion 53 is good.

[0084] [Effects of the Implementation Method]

[0085] The following effects can be achieved in the implementation method.

[0086] (1) When the bushing 51 moves axially toward the vortex member 26 between the top end 15e of the rotating shaft 15 and the vortex member 26, the bushing flange 53 abuts against the bearing flange 58. Therefore, even if the bushing 51 moves axially toward the vortex member 26 between the top end 15e of the rotating shaft 15 and the vortex member 26, it is possible to avoid the bushing 51 abutting against the vortex member 26. Therefore, it is possible to avoid the problem of wear between the vortex member 26 and the bushing 51 caused by the bushing 51 abutting against the vortex member 26. Therefore, for example, it is not necessary to provide additional components to limit the movement of the bushing 51 toward the vortex member 26 axially on the rotating shaft 15, or to provide additional components with high wear resistance different from the sliding bearing 56 between the bushing 51 and the vortex member 26 axially on the rotating shaft 15.

[0087] Furthermore, a groove 61 extending from the air supply passage 46 toward the bearing flange portion 58 is formed in the bearing housing portion 57. Therefore, oil from the air supply passage 46 can be easily supplied to the bearing flange portion 58 via the groove 61. Also, a notch 62 communicating with the groove 61 and supplying oil toward the outer periphery of the bearing flange portion 58 is formed in the bearing flange portion 58. Therefore, oil supplied from the groove 61 to the bearing flange portion 58 can be easily supplied to the outer periphery of the bearing flange portion 58 via the notch 62. As a result, even when the bushing flange portion 53 abuts against the bearing flange portion 58, good lubrication between the bearing flange portion 58 and the bushing flange portion 53 can be achieved. Through the above, the durability of the scroll compressor 10 can be improved while reducing the number of components.

[0088] (2) The air supply passage 46 opens at a point on the bottom surface 47a of the recess 47, across the second straight line L12, on the side opposite to the groove 61. This allows the distance from the air supply passage 46 to the groove 61 to be as far as possible, thus facilitating the supply of oil from the air supply passage 46 to the inner circumferential surface of the bearing housing 57. As a result, good lubrication is achieved between the bearing housing 57 and the bushing housing 52. Therefore, the durability of the scroll compressor 10 can be further improved.

[0089] (3) The bearing flange 58 abuts against the end face 26f of the base plate to press the swirling scroll member 26 toward the fixed scroll member 25, and abuts against the bushing flange 53 to press the bushing 51 toward the top end 15e of the rotating shaft 15. This allows the bushing 51 to be positioned axially on the rotating shaft 15. Therefore, it is possible to suppress the bushing 51 from moving axially between the top end 15e of the rotating shaft 15 and the swirling scroll member 26 on the rotating shaft 15.

[0090] (4) The bearing flange portion 58 has a first extension portion 59 and a second extension portion 60. The first extension portion 59 extends in an arc shape from the bearing sleeve portion 57 toward the radially outer side of the rotating shaft 15 and abuts against the bushing flange portion 53. The second extension portion 60 extends in an arc shape obliquely toward the substrate end face 26f from the end of the first extension portion 59 on the side opposite to the bearing sleeve portion 57 and abuts against the substrate end face 26f. This configuration is suitable for positioning the bushing 51 in the axial direction of the rotating shaft 15.

[0091] (5) Since it is not necessary to provide a high wear-resistant component different from the sliding bearing 56 between the bushing 51 and the scroll component 26 in the axial direction of the rotating shaft 15, it is possible to miniaturize the size of the scroll compressor 10 in the axial direction of the rotating shaft 15.

[0092] [Example of Change]

[0093] Furthermore, the above embodiments can be implemented by modification as follows. The above embodiments and the following modifications can be combined with each other within the scope of technical inconsistency.

[0094] ○ For example Figure 6 As shown, the first extension 59 may also extend in an arc shape from the bearing sleeve portion 57 toward the radially outer side of the rotating shaft 15 and abut against the end face 26f of the substrate. The second extension 60 may also extend in an arc shape obliquely toward the bushing flange portion 53 from the end of the first extension 59 on the side opposite to the bearing sleeve portion 57 and abut against the bushing flange portion 53. This configuration is suitable for positioning the bushing 51 in the axial direction of the rotating shaft 15.

[0095] In one embodiment, the bearing flange 58 may not press the swirling scroll 26 toward the fixed scroll 25, nor press the bushing 51 toward the top end 15e of the rotating shaft 15.

[0096] In one embodiment, the air supply passage 46 may also open at a location on the bottom surface 47a of the recess 47, closer to the groove 61 than the second straight line L12.

[0097] In this embodiment, when viewed along the axial direction of the rotation axis 15, the angle between the first notch edge 621 and the second notch edge 622 of the notch 62 may be an acute angle.

[0098] In one embodiment, the notch 62 may also be cut from the second extension 60 when viewed along the axial direction of the rotation axis 15.

[0099] In this embodiment, the shape of the notch 62 is not particularly limited as long as it can communicate with the groove 61 and supply oil toward the outer periphery of the bearing flange portion 58.

[0100] In one embodiment, the sliding bearing 56 is non-annular, formed by bending a strip of metal into an arc shape, but it is not limited to this and can also be an annular shape that is continuous throughout the entire circumference. In this case, the groove 61 can simply extend by recessing a portion of the inner circumferential surface of the bearing sleeve portion 57 to supply oil from the air supply passage 46 toward the bearing flange portion 58.

[0101] In one embodiment, the eccentric shaft 50 may also be separate from the rotating shaft 15, rather than being integrally formed with it. In this case, the eccentric shaft 50 is mounted on the top end 15e of the rotating shaft 15.

[0102] In another embodiment, the gas supply passage 46 may be formed on the vortex member 26 such that the first end of the gas supply passage 46 is opened on the end face of the vortex wall 26b in the vortex substrate 26a and only penetrates the vortex substrate 26a.

[0103] In this embodiment, the counterweight 55 may also be separate from the bushing 51.

[0104] In this embodiment, the scroll compressor 10 may also be a type that is not driven by the motor 22, for example, it may be a type that is driven by the vehicle's engine.

[0105] In this embodiment, the scroll compressor 10 is used in a vehicle air conditioning system, but is not limited thereto. In short, the scroll compressor 10 only needs to compress the refrigerant, and its application can be appropriately changed.

[0106] In this embodiment, the object compressed by the scroll compressor 10 is not limited to a refrigerant; for example, it may also be a fluid such as air.

Claims

1. A scroll compressor, comprising: A housing having an inlet for drawing in refrigerant and an outlet for discharging refrigerant; A rotating shaft, which is housed within the housing and rotatably supported by the housing; and The compression mechanism includes a fixed scroll member fixed to the housing and a rotary scroll member that revolves by the rotation of the rotating shaft. The rotating shaft is provided with an eccentric shaft that protrudes from the top of the rotating shaft and extends parallel to the rotating shaft at a position eccentric to the central axis of the rotating shaft. The fixed vortex member has a fixed base plate, a fixed vortex wall erected from the fixed base plate, and a fixed outer peripheral wall erected from the fixed base plate and surrounding the fixed vortex wall. The vortex component has a vortex base plate facing the fixed base plate, and a vortex wall that rises from the vortex base plate toward the fixed base plate and revolves inside the fixed outer peripheral wall. The compression mechanism includes a compression chamber divided by the fixed base plate, the fixed vortex wall, the gyratory base plate, and the gyratory vortex wall, through which the refrigerant is compressed by the engagement of the fixed vortex wall and the gyratory vortex wall. The housing has a shaft support housing disposed on the side opposite to the fixed base plate relative to the rotating base plate and supporting the rotation axis. A back pressure chamber is formed between the end face of the gyratory substrate on the side opposite to the fixed substrate (i.e., the substrate end face) and the shaft support housing, for introducing refrigerant to exert force on the gyratory substrate toward the fixed substrate. The swirling vortex component has an oil supply hole that opens toward the back pressure chamber and supplies oil to the back pressure chamber. The eccentric shaft is inserted into a bushing that can swing about the eccentric shaft. A bottomed cylindrical recess for arranging the bushing is formed on the end face of the substrate. A sliding bearing is disposed on the inner circumferential surface that divides the recess, supporting the bushing so that it can rotate. The oil supply hole opens on the bottom surface that divides the recess. The bushing has a bushing sleeve portion disposed inside the sliding bearing. The sliding bearing has a bearing sleeve portion disposed on the inner circumferential surface. Its features are, The bushing has a bushing flange that protrudes radially outward from the bushing sleeve portion toward the axis of rotation. The sliding bearing has a bearing flange portion that protrudes radially outward from the bearing sleeve portion and is disposed between the end face of the base plate and the bushing flange portion. A groove is formed in the bearing sleeve portion, extending in such a way as to supply oil from the oil supply hole toward the bearing flange portion. A notch is formed in the bearing flange portion that communicates with the groove and supplies oil toward the outer periphery of the bearing flange portion.

2. The scroll compressor according to claim 1, characterized in that, When viewed along the axial direction of the rotation axis, if the straight line connecting the center of the recess and the oil supply hole is designated as the first straight line, and the straight line passing through the center of the recess and extending in a direction orthogonal to the first straight line is designated as the second straight line, then the oil supply hole opens at a location on the bottom surface opposite to the groove, separated by the second straight line.

3. The scroll compressor according to claim 1 or 2, characterized in that, The bearing flange abuts against the end face of the substrate to press the swirling scroll toward the fixed scroll, and abuts against the bushing flange to press the bushing toward the top of the rotating shaft.

4. The scroll compressor according to claim 3, characterized in that, The bearing flange portion has: A first extension, which extends in an arc shape from the bearing sleeve portion toward the radially outward portion and abuts against the bushing flange portion; and The second extension extends obliquely in an arc shape from the end of the first extension on the side opposite to the bearing cylinder portion toward the end face of the substrate and abuts against the end face of the substrate.

5. The scroll compressor according to claim 3, characterized in that, The bearing flange portion has: A first extension portion, the first extension portion extending in an arc shape from the bearing sleeve portion outward in a radial direction and abutting against the end face of the substrate; and The second extension extends obliquely in an arc shape from the end of the first extension on the side opposite to the bearing sleeve portion toward the bushing flange portion and abuts against the bushing flange portion.

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