SCROLL COMPRESSOR

Abstract

A scroll compressor (10) has a housing (11), a rotating shaft (15), and a compression mechanism (C1). The rotating shaft (15) has an eccentric shaft (50). The compression mechanism (C1) has a compression chamber (27). The housing (11) has a shaft support housing (13). A refrigerant is introduced into a back-pressure chamber (45). The rotating screw (26) has an oil supply port (26). The eccentric shaft (50) is inserted into a bushing (51). The bushing (51) has a tubular bushing section (52) and a bushing flange section (53). The plain bearing (56) has a tubular bearing section (57) and a bearing flange section (58). A groove (61) is formed in the tubular bearing section (57). A cutout (62), through which the oil is supplied in the direction of an outer circumferential edge of the bearing flange section (58), is formed in the bearing flange section (58) and is connected to the groove (61).

Description

TECHNICAL BACKGROUND

[0001] The present invention relates to a scroll compressor.

[0002] The scroll compressor has a housing, a rotating shaft, and a compression mechanism. The housing has an intake port and a discharge port. Refrigerant is drawn in through the intake port and discharged through the discharge port. The rotating shaft is housed within the casing and is rotatably supported by the casing. The rotating shaft has an eccentric shaft that projects from a distal end of the shaft. The eccentric shaft extends parallel to the rotating shaft at a position offset from the axial centerline of the shaft.

[0003] The compression mechanism has a fixed screw and a rotating screw. The fixed screw is fixed to the housing. The fixed screw has a fixed screw base plate, a fixed screw spiral wall, and a fixed screw outer circumferential wall. The fixed screw spiral wall projects from the fixed screw base plate. The fixed screw outer circumferential wall projects from the fixed screw base plate and surrounds the fixed screw spiral wall. The rotating screw rotates with the rotation of the drive shaft. The rotating screw has a rotating screw base plate and a rotating screw spiral wall. The rotating screw base plate faces the fixed screw base plate. The rotating screw spiral wall projects from the rotating screw base plate toward the fixed screw base plate and rotates inside the fixed screw outer circumferential wall.

[0004] A compression chamber is formed within the compression mechanism. The compression chamber is defined by the fixed screw base plate, the fixed screw spiral wall, the rotating screw base plate, and the rotating screw spiral wall. The refrigerant, which has been drawn into the compression chamber, is compressed by the engagement of the fixed screw spiral wall with the rotating screw spiral wall.

[0005] The housing has a shaft support housing. The shaft support housing is positioned on one side opposite the fixed screw base plate relative to the rotating screw base plate. The shaft support housing supports the rotating shaft. A back pressure chamber is formed between the shaft support housing and a base plate end face of the rotating screw base plate, opposite the fixed screw base plate. The refrigerant for forcing the rotating screw base plate towards the fixed screw base plate is introduced into the back pressure chamber. An oil supply hole is formed in the rotating screw. The oil supply hole opens towards the back pressure chamber, and oil is supplied to the back pressure chamber through this hole.

[0006] The eccentric shaft is inserted into a bushing. The bushing is pivotable around the eccentric shaft. A recess, which has a tubular shape with a base, is formed in the end face of the base plate. The bushing is positioned in the recess. The oil supply hole opens in a base surface that defines the recess.

[0007] For example, as disclosed in Japanese patent application No. 2014-173436, a sliding bearing is arranged on an inner circumferential surface that defines the recess. The sliding bearing rotatably supports the bushing. The bushing has a tubular bushing section, which is formed in a tubular shape and is arranged inside the sliding bearing. The sliding bearing has a tubular bearing section that is arranged on the inner circumferential surface of the recess.

[0008] In such a scroll compressor, the bushing can move axially towards the rotating screw between the distal end of the rotating shaft and the rotating screw. If the bushing moves axially between the rotating shaft and the rotating screw, it can come into contact with the screw. This contact causes abrasion between the screw and the bushing, reducing the service life of the scroll compressor.

[0009] For example, consideration is being given to separately providing a component to restrict the movement of the bushing towards the rotating screw in the axial direction of the rotating shaft, and to providing a component with high wear resistance between the bushing and the rotating screw in the axial direction of the rotating shaft, which differs from the plain bearing. However, these are not preferred because they increase the number of components. Therefore, it was desirable to improve the service life of the scroll compressor without increasing the number of components. SUMMARY

[0010] According to one aspect of the present invention, a scroll compressor is provided, comprising a housing with an inlet port through which a refrigerant is drawn in and a discharge port through which the refrigerant is discharged, a rotating shaft housed in the housing and rotatably supported by the housing, and a compression mechanism comprising a fixed screw fixed to the housing and a rotating screw that rotates with the rotation of the rotating shaft. The rotating shaft has an eccentric shaft projecting from a distal end of the rotating shaft and extending parallel to the rotating shaft at a position offset from an axial centerline of the rotating shaft.The fixed screw has a fixed screw base plate, a fixed screw spiral wall projecting from the fixed screw base plate, and a fixed screw outer circumferential wall projecting from the fixed screw base plate and surrounding the fixed screw spiral wall. The rotating screw has a rotating screw base plate facing the fixed screw base plate and a rotating screw spiral wall projecting from the rotating screw base plate towards the fixed screw base plate and running inside the fixed screw outer circumferential wall. The compression mechanism has a compression chamber defined by the fixed screw base plate, the fixed screw spiral wall, the rotating screw base plate, and the rotating screw spiral wall, in which the refrigerant is compressed by the engagement of the fixed screw spiral wall with the rotating screw spiral wall.The housing has a shaft support housing located on one side opposite the fixed screw base plate relative to the rotating screw base plate, and supporting the rotating shaft. The refrigerant is introduced into a back-pressure chamber formed between a base plate end face of the rotating screw base plate, opposite the fixed screw base plate, and the shaft support housing, with the refrigerant forcing the rotating screw base plate towards the fixed screw base plate. The rotating screw has an oil supply port that opens towards the back-pressure chamber, through which oil is supplied. The eccentric shaft is inserted into a bushing that is pivotable around the eccentric shaft. The base plate end face has a recess formed in a tubular shape with a bottom, in which the bushing is located.The recess is defined by an inner circumferential surface on which a sliding bearing, rotatably supporting the bushing, is arranged. The recess is defined by a bottom surface in which the oil supply hole opens. The bushing has a tubular bushing section located inside the sliding bearing. The sliding bearing has a bearing flange section that projects radially outward from the tubular bearing section and is located between the base plate end face and the bushing flange section. A groove is formed in the tubular bearing section and extends such that the oil is supplied from the oil supply hole toward the bearing flange section through the groove. A cutout, through which the oil is supplied toward an outer circumferential edge of the bearing flange section, is formed in the bearing flange section and is connected to the groove.

[0011] Other aspects and advantages of the invention will be evident from the following description together with the accompanying drawings, which exemplify the principles of the invention. BRIEF DESCRIPTION OF THE DRAWINGS

[0012] The invention, together with its tasks and advantages, can best be understood by referring to the following description of exemplary embodiments together with the accompanying drawings. Fig. Figure 1 is a cross-sectional view of a scroll compressor according to an exemplary embodiment; Fig. 2 is an enlarged cross-sectional view showing part of the scroll compressor; Fig. Figure 3 is a perspective view showing a rotating worm and a sliding bearing; Fig. 4 is a perspective view showing the rotating worm and the sliding bearing; Fig. 5 is a front view showing the orbital worm and the sliding bearing; and Fig. Figure 6 is an enlarged cross-sectional view showing part of a scroll compactor according to a modified example. DETAILED DESCRIPTION OF THE EXECUTION EXAMPLES

[0013] The following describes an exemplary embodiment of a scroll compressor with reference to Fig. 1, Fig. 2, Fig. 3, Fig. 4 to Fig. 5. The scroll compressor in the present embodiment is used, for example, in a vehicle air conditioning system. <Grundlegende Gestaltung des Scrollverdichters>

[0014] As in Fig. As shown in Figure 1, the scroll compressor 10 has a housing 11, which is designed in a tubular shape. The housing 11 comprises a motor housing 12, a shaft support housing 13, and a discharge housing 14. The motor housing 12, the shaft support housing 13, and the discharge housing 14 are made of metal, such as aluminum. The scroll compressor 10 also has a rotating shaft 15. The rotating shaft 15 is housed within the housing 11.

[0015] The motor housing 12 has an end wall 12a formed in a plate shape and a circumferential wall 12b formed in a tubular shape. The circumferential wall 12b is tubular and extends from an outer circumferential section of the end wall 12a. An axial direction of the circumferential wall 12b coincides with an axial direction of the rotating shaft 15. The motor housing 12 has a plurality of internally threaded holes 12c. The internally threaded holes 12c are formed in an open end of the circumferential wall 12b. It should be noted that Fig. Figure 1 shows only one of the internal threaded holes 12c for the purpose of description. The motor housing 12 also has an intake port 12h. That is, the housing 11 has the intake port 12h. A refrigerant is drawn through the intake port 12h. The intake port 12h is formed in a section of the circumferential wall 12b that is located closer to the end wall 12a. An inner side of the motor housing 12 and an outer side of the motor housing 12 are connected to each other by the intake port 12h.

[0016] The motor housing 12 has a bearing support section 12d, which is cylindrical in shape. The bearing support section 12d projects from a central section of an inner surface of the end wall 12a. A first end section of the rotating shaft 15, which is an end section of the rotating shaft 15 in the axial direction, is inserted into the bearing support section 12d. The scroll compressor 10 has a bearing 16. The bearing 16 is, for example, a rolling bearing. The bearing 16 is located between an inner circumferential surface of the bearing support section 12d and an outer circumferential surface of the first end section of the rotating shaft 15. The first end section of the rotating shaft 15 is rotatably supported by the motor housing 12 via the bearing 16.

[0017] The shaft support housing 13 has an end wall 17, which is formed in a plate shape, and a circumferential wall 18, which is formed in a tubular shape. The circumferential wall 18 is tubular and extends from an outer circumferential section of the end wall 17. An axial direction of the circumferential wall 18 coincides with the axial direction of the rotating shaft 15. Furthermore, the shaft support housing 13 has a flange wall 19, which is formed in an annular shape. The flange wall 19 extends outwards in a radial direction along the rotating shaft 15 from an end of the outer circumferential surface of the circumferential wall 18, opposite the end wall 17.

[0018] The shaft support housing 13 has an insertion hole 17a, which is formed in the shape of a circular hole. The insertion hole 17a is formed in a central section of the end wall 17. The insertion hole 17a extends through the end wall 17 in a thickness direction from it. The rotating shaft 15 is inserted through the insertion hole 17a. A distal end 15e in a second end section of the rotating shaft 15, which is the other end section of the rotating shaft 15 in the axial direction from it, is located inside the circumferential wall 18.

[0019] The scroll compressor 10 has a bearing 21. The bearing 21 is, for example, a rolling bearing. The bearing 21 is located between an inner circumferential surface of the circumferential wall 18 and an outer circumferential surface of the rotating shaft 15. The rotating shaft 15 is rotatably supported by the shaft support housing 13 via the bearing 21. That is, the shaft support housing 13 rotatably supports the rotating shaft 15. Thus, the rotating shaft 15 is rotatably supported by the housing 11.

[0020] The shaft support housing 13 has a plurality of bolt insertion holes 19a. The bolt insertion holes 19a are formed in an outer circumferential section of the flange wall 19. The bolt insertion holes 19a extend through the flange wall 19 in a thickness direction from it. Each of the bolt insertion holes 19a of the flange wall 19 is connected to a corresponding internal threaded hole 12c of the motor housing 12. It should be noted that Fig. 1 only one of the bolt insertion holes 19a is shown for the purpose of description.

[0021] The scroll compressor 10 has a motor chamber 20. The motor chamber 20 is defined by the motor housing 12 and the shaft support housing 13. The motor housing 12, together with the shaft support housing 13, defines the motor chamber 20. Thus, the motor chamber 20 is formed within the housing 11. The motor chamber 20 is connected to the intake port 12h. The refrigerant is drawn into the motor chamber 20 through the intake port 12h. Consequently, the motor chamber 20 is a region at an intake pressure.

[0022] The scroll compressor 10 has a motor 22. The motor 22 is housed in the motor chamber 20. The motor 22 has a stator 23, which is tubular in shape, and a rotor 24, which is also tubular in shape. The rotor 24 is located inside the stator 23. The rotor 24 rotates together with the rotating shaft 15. The stator 23 surrounds the rotor 24. The rotor 24 has a rotor core 24a, which is fixed to the rotating shaft 15, and a plurality of permanent magnets, not shown, which are provided in the rotor core 24a.

[0023] The stator 23 has a stator core 23a, which is tubular in shape, and a motor coil 23b. The stator core 23a is fixed to an inner circumferential surface of the circumferential wall 12b of the motor housing 12. The motor coil 23b is wound around the stator core 23a. Power, controlled by an inverter (not shown), is supplied to the motor coil 23b, causing the rotor 24 to rotate. As a consequence, the rotating shaft 15 rotates in unison with the rotor 24. Thus, the motor 22 rotates the rotating shaft 15.

[0024] The scroll compressor 10 has a compression mechanism C1. The compression mechanism C1 has a fixed screw 25 and a rotating screw 26. That is, the scroll compressor 10 has the fixed screw 25 and the rotating screw 26. The compression mechanism C1 is of a scroll type. The rotating screw 26 rotates relative to the fixed screw 25 with the rotation of the rotating shaft 15.

[0025] The fixed screw 25 has a fixed screw base plate 25a, a fixed screw spiral wall 25b, and a fixed screw outer circumferential wall 25c. The fixed screw base plate 25a is circular in shape. A discharge port 25h is located at the center of the fixed screw base plate 25a. The discharge port 25h is circular in shape. The discharge port 25h extends through the fixed screw base plate 25a in a thickness direction. The fixed screw spiral wall 25b projects from the fixed screw base plate 25a. The fixed screw outer circumferential wall 25c projects from an outer circumferential section of the fixed screw base plate 25a. The fixed screw outer circumferential wall 25c surrounds the fixed screw spiral wall 25b.

[0026] The scroll compressor 10 has a valve mechanism 25v. The valve mechanism 25v is mounted on a surface of the fixed screw base plate 25a opposite the fixed screw spiral wall 25b. The valve mechanism 25v is designed to open and close the discharge port 25h.

[0027] The rotating screw 26 has a rotating screw base plate 26a and a rotating screw spiral wall 26b. The rotating screw base plate 26a is circular in shape. The rotating screw base plate 26a faces the fixed screw base plate 25a. The rotating screw spiral wall 26b projects from the rotating screw base plate 26a towards the fixed screw base plate 25a. The rotating screw spiral wall 26b engages with the fixed screw spiral wall 25b. The rotating screw 26 is located inside the fixed screw outer circumferential wall 25c. The rotating screw 26 runs inside the fixed screw outer circumferential wall 25c. That is, the rotating screw spiral wall 26b runs inside the fixed screw outer circumferential wall 25c. A distal end surface of the solid spiral wall 25b is in contact with the circumferential base plate 26a.A distal end surface of the circumferential snail spiral wall 26b is in contact with the solid snail base plate 25a.

[0028] A compression chamber 27 is formed in the compression mechanism C1. The compression chamber 27 is defined by the fixed screw base plate 25a, the fixed screw spiral wall 25b, the rotating screw base plate 26a, and the rotating screw spiral wall 26b. Accordingly, the compression chamber 27 is defined between the fixed screw 25 and the rotating screw 26. The refrigerant drawn into the compression chamber 27 is compressed by the engagement of the fixed screw spiral wall 25b with the rotating screw spiral wall 26b.

[0029] The rotating worm base plate 26a has a hub section 28. The hub section 28 projects from a first surface 26e, which is a surface of the rotating worm base plate 26a opposite the fixed worm base plate 25a. The hub section 28 projects from a central section of the first surface 26e towards the shaft support housing 13. The shaft support housing 13 is arranged on one side opposite the fixed worm base plate 25a relative to the rotating worm base plate 26a. An axial direction of the hub section 28 coincides with the axial direction of the rotating shaft 15. The first surface 26e and a distal end surface 28a of the hub section 28 form a base plate end surface 26f of the rotating worm base plate 26a, which is an end surface opposite the fixed worm base plate 25a. An interior of the hub section 28 corresponds to a recess 47, which is formed in the base plate end surface 26f.Thus, the recess 47, which has a tubular shape with a bottom, is formed in the base plate end surface 26f.

[0030] The circumferential worm base plate 26a has a plurality of groove sections 26d. The plurality of groove sections 26d is formed around the hub section 28 in the first surface 26e of the circumferential worm base plate 26a. The plurality of groove sections 26d is arranged at predetermined intervals in a circumferential direction of the rotating shaft 15. It should be noted that Fig. Figure 1 shows only one of the groove sections 26d for the purpose of description. Ring-shaped ring components 29 are each fitted into a corresponding groove section 26d. Pins 30 are each inserted into a corresponding ring component 29. The pins 30 extend from an end surface 13e of the shaft support housing 13, which is closer to the rotating worm 26.

[0031] The scroll compressor 10 has an elastic plate 31. The elastic plate 31 is formed in an annular shape. The elastic plate 31 is held between the end face 13e of the shaft support housing 13 and an open end face of the fixed outer circumferential wall 25c of the screw. The elastic plate 31 always pushes the rotating screw 26 towards the fixed screw 25.

[0032] The discharge housing 14 has an end wall 14a, which is plate-shaped, and a circumferential wall 14b, which is tubular. The circumferential wall 14b is tubular and extends from an outer circumferential section of the end wall 14a. The axial direction of the circumferential wall 14b coincides with the axial direction of the rotating shaft 15. The circumferential wall 14b surrounds the fixed screw 25. Consequently, the fixed screw 25 is housed within the housing 11.

[0033] The dispensing housing 14 has a plurality of bolt insertion holes 14c. The bolt insertion holes 14c are formed in the circumferential wall 14b. It should be noted that Fig. Figure 1 shows only one of the bolt insertion holes 14c for the purpose of description. The bolt insertion holes 14c are connected to the corresponding bolt insertion holes 19a in the flange wall 19.

[0034] Bolts B1, inserted through the corresponding bolt insertion holes 14c, are inserted through the corresponding bolt insertion holes 19a of the flange wall 19 and are then screwed into the corresponding internal threaded holes 12c of the motor housing 12. These bolts B1 connect the shaft support housing 13 to the circumferential 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. Thus, the motor housing 12, the shaft support housing 13, and the discharge housing 14 are arranged in this order along the axial direction of the rotating shaft 15. The fixed worm 25 is held between the end wall 14a of the discharge housing 14 and the shaft support housing 13. The fixed worm 25 is therefore fixed to the housing 11.

[0035] The scroll compressor 10 has an intake passage 35. The intake passage 35 has a first groove 36, a first hole 37, a second groove 38, and a second hole 39. The first groove 36 is formed in a section of the inner circumferential surface of the circumferential wall 12b of the motor housing 12. The first groove 36 opens at an open end of the circumferential wall 12b. The first hole 37 is formed in the outer circumferential section of the flange wall 19 of the shaft support housing 13. The first hole 37 extends through the flange wall 19 in the thickness direction of the flange wall 19. The first hole 37 is connected to the first groove 36. The second groove 38 is formed in a section of an inner circumferential surface of the circumferential wall 14b of the discharge housing 14. The second groove 38 is connected to the first hole 37. The second hole 39 is formed in the solid outer circumferential wall 25c of the solid screw 25.The second hole 39 extends through the solid outer circumferential wall 25c in a thickness direction from it. The second hole 39 is connected to the second groove 38. The second hole 39 is connected to an outermost circumferential section of the compression chamber 27.

[0036] The refrigerant in the motor chamber 20 flows through the first groove 36, the first hole 37, the second groove 38, and the second hole 39 and is drawn into the compression chamber 27. The refrigerant drawn into the compression chamber 27 is compressed by the rotating motion of the screw 26. Thus, the compression mechanism C1 compresses the refrigerant that has been drawn into the housing 11.

[0037] The scroll compressor 10 has a discharge chamber 40. The discharge chamber 40 is defined between the fixed screw base plate 25a and the end wall 14a of the discharge housing 14. The discharge chamber 40 is connected to the discharge port 25h. The refrigerant that has been compressed in the compression chamber 27 is discharged into the discharge chamber 40. The discharge housing 14 has a discharge port 14h. That is, the housing 11 has the discharge port 14h. The discharge port 14h is formed in the end wall 14a of the discharge housing 14. The discharge port 14h is connected to the discharge chamber 40. The refrigerant in the discharge chamber 40 is discharged through the discharge port 14h to the outside of the scroll compressor 10.

[0038] A back pressure chamber 45 is defined between the rotating screw base plate 26a of the rotating screw 26 and the shaft support housing 13. The back pressure chamber 45 is formed on one side opposite the fixed screw base plate 25a relative to the rotating screw base plate 26a in the housing 11. Thus, the 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 circumferential wall 18 of the shaft support housing 13 is part of the back pressure chamber 45. A gap between the elastic plate 31 and the shaft support housing 13 is also part of the back pressure chamber 45.

[0039] The scroll compressor 10 has an air supply passage 46. The air supply passage 46 is formed in the rotating screw 26. A first end of the air supply passage 46 opens in a distal end of the rotating screw spiral wall 26b. The first end of the air supply passage 46 is able to communicate with the compression chamber 27. A second end of the air supply passage 46 opens in a base surface 47a that defines the recess 47. The second end of the air supply passage 46 is connected to the counter-pressure chamber 45. The air supply passage 46 extends through an inner end section of the rotating screw spiral wall 26b, which is formed in a spiral shape extending radially inward toward a center of the rotating screw 26, and the rotating screw base plate 26a. The air supply passage 46 is a through hole that has a circular hole shape.

[0040] A portion of the refrigerant compressed in the compression chamber 27 is fed to the counter-pressure chamber 45 through the air supply passage 46. As a result, the pressure in the counter-pressure chamber 45 is higher than that in the motor chamber 20. When the pressure in the counter-pressure chamber 45 increases, the rotating screw base plate 26a is forced towards the fixed screw base plate 25a, so that the distal end of the rotating screw spiral wall 26b is pressed against the fixed screw base plate 25a. Thus, the refrigerant is introduced into the counter-pressure chamber 45 to force the rotating screw base plate 26a towards the fixed screw base plate 25a.

[0041] Furthermore, an oil is supplied to the counter-pressure chamber 45 along with the refrigerant through the air supply passage 46. Consequently, the air supply passage 46 also serves as an oil supply port for supplying the oil to the counter-pressure chamber 45. Thus, the oil supply port, which opens towards the counter-pressure chamber 45 and through which the oil is supplied to the counter-pressure chamber 45, is formed in the rotating screw 26. The air supply passage 46, as the oil supply port, opens in the base surface 47a, which defines the recess 47.

[0042] The rotating shaft 15 has an eccentric shaft 50. The eccentric shaft 50 projects from the distal end 15e of the rotating shaft 15 and extends parallel to the rotating shaft 15 at a position offset from the axial centerline L1 of the rotating shaft 15. The eccentric shaft 50 is formed integrally with the rotating shaft 15. The axial direction of the eccentric shaft 50 coincides with the axial direction of the rotating shaft 15. The eccentric shaft 50 projects from the distal end 15e of the rotating shaft 15 in the direction of the rotating worm 26. The eccentric shaft 50 is inserted into the recess 47. <buchse>

[0043] As in Fig. As shown in Figure 2, the eccentric shaft 50 is inserted into a bushing 51. The bushing 51 has a tubular bushing section 52 and a bushing flange section 53. The eccentric shaft 50 is inserted into the tubular bushing section 52. The tubular bushing section 52 is arranged inside the recess 47. That is, the bushing 51 is arranged in the recess 47.

[0044] An end section of the tubular bushing section 52 extends from the hub section 28, opposite the circumferential worm base plate 26a. The bushing flange section 53 is formed in an annular shape, projecting outwards from the end section of the tubular bushing section 52, opposite the circumferential worm base plate 26a. The bushing flange section 53 projects outwards from the tubular bushing section 52 in the radial direction of the rotating shaft 15. The bushing flange section 53 overlaps the distal end surface 28a of the hub section 28 in the axial direction of the hub section 28. The bushing 51 is pivotable around the eccentric shaft 50.

[0045] The scroll compressor 10 has a counterweight 55. The counterweight 55 is formed integrally with the bushing 51. The counterweight 55 projects outwards from a section of the outer circumferential surface of the bushing flange section 53. The counterweight 55 is located inside the circumferential wall 18 of the shaft support housing 13. <gleitlager>

[0046] A sliding bearing 56 is arranged on an inner circumferential surface 47b, which defines the recess 47. The sliding bearing 56 has a tubular shape. The sliding bearing 56 is formed into an arc shape by bending a strip-shaped sheet material made of metal. That is, the sliding bearing 56 does not have a ring-shaped form.

[0047] The plain bearing 56 has a tubular bearing section 57 and a bearing flange section 58. The tubular bearing section 57 is arranged on the inner circumferential surface 47b of the recess 47. The tubular bearing section 57 is located between the inner circumferential surface 47b of the recess 47 and the outer circumferential surface of the tubular bushing section 52. The tubular bushing section 52 is located inside the plain bearing 56. The plain bearing 56 rotatably supports the bushing 51.

[0048] An end section of the tubular bearing section 57 extends from the recess 47, opposite the circumferential worm base plate 26a. The bearing flange section 58 is formed in an annular shape, projecting outwards from the end section of the tubular bearing section 57, opposite the circumferential worm base plate 26a. The bearing flange section 58 projects outwards from the tubular bearing section 57 in the radial direction of the rotating shaft 15. The bearing flange section 58 is arranged between the distal end face 28a of the hub section 28 and the bushing flange section 53. That is, the bearing flange section 58 is arranged between the base plate end face 26f and the bushing flange section 53.

[0049] The bearing flange section 58 has a first extension section 59 and a second extension section 60. The first extension section 59 is formed in an arc shape that extends outwards from the tubular bearing section 57 in the radial direction of the rotating shaft 15. The first extension section 59 extends along the bushing flange section 53. The first extension section 59 is in contact with the bushing flange section 53. The second extension section 60 is formed in an arc shape that extends and is inclined from one end of the first extension section 59 opposite the tubular bearing section 57 towards the base plate end face 26f. The second extension section 60 is in contact with the distal end face 28a of the hub section 28. That is, the second extension section 60 is in contact with the base plate end face 26f.The bearing flange section 58 is in contact with the base plate end surface 26f and presses the rotating screw 26 against the fixed screw 25 and is also in contact with the bushing flange section 53 and presses the bushing 51 against the distal end 15e of the rotating shaft 15.

[0050] The rotation of the rotating shaft 15 is transmitted to the rotating screw 26 via the eccentric shaft 50, the bushing 51, and the plain bearing 56. This causes the rotating screw 26 to rotate about its own axis. The pins 30 then come into contact with the inner circumferential surfaces of the ring components 29, which prevents the rotating screw 26 from rotating about its own axis and allows it to only complete its rotation. Thus, the rotating screw 26 continues to rotate, with the rotating screw spiral wall 26b in contact with the fixed screw spiral wall 25b. The volume of the compression chamber 27 decreases with the rotation of the rotating screw 26, compressing the refrigerant in the compression chamber 27. The rotating screw 26 rotates inside the fixed screw outer circumferential wall 25c with the rotation of the rotating shaft 15.The counterweight 55 counteracts a centrifugal force acting on the rotating screw 26 during its rotation. This reduces the degree of imbalance in the rotating screw 26. <nut>

[0051] As in Fig. 3 and Fig. As shown in Figure 4, a groove 61 is formed in the tubular bearing section 57. The groove 61 is formed between a first edge 571 of the tubular bearing section 57, located on one side in a circumferential direction of the tubular bearing section 57, and a second edge 572 of the tubular bearing section 57, located on the other side in the circumferential direction of the tubular bearing section 57. The groove 61 is a gap between the first edge 571 and the second edge 572. The groove 61 extends from a first edge to a second edge in an axial direction of the tubular bearing section 57. The groove 61 extends such that the oil is supplied from the air supply passage 46 towards the bearing flange section 58 through the groove 61.

[0052] As in Fig. As shown in Figure 5, from the perspective in the axial direction of the rotating shaft 15, a straight line connecting the center P10 of the recess 47 with the air supply passage 46 is defined as a first straight line L11. A straight line passing through the center P10 of the recess 47 and extending perpendicular to the first straight line L11 is defined as a second straight line L12. Here, the air supply passage 46 opens in the bottom surface 47a across the second straight line L12 when positioned opposite the groove 61. <ausschnitt>

[0053] The bearing flange section 58 has a cutout 62. The cutout 62 is formed by a first cutout edge 621 and a second cutout edge 622. The first cutout edge 621 is continuous with the first edge 571. The second cutout edge 622 is continuous with the second edge 572. That is, the cutout 62 is in contact with the groove 61. The first cutout edge 621 connects the first edge 571 to an outer circumferential edge of the bearing flange section 58. The second cutout edge 622 connects the second edge 572 to the outer circumferential edge of the bearing flange section 58. The distance between the first cutout edge 621 and the second cutout edge 622 increases with the extension of the first cutout edge 621 and the second cutout edge 622 away from the groove 61.The cutout 62 is designed such that the angle between the first cutout edge 621 and the second cutout edge 622 is an obtuse angle when viewed in the axial direction of the rotating shaft 15. The cutout 62 extends over the first extension section 59 and the second extension section 60, when viewed in the axial direction of the rotating shaft 15. The oil is supplied to the outer circumferential edge of the bearing flange section 58 through the cutout 62. [Operation of the exemplary embodiment]

[0054] The following describes one operation of the exemplary embodiment.

[0055] In such a scroll compressor 10, the bushing 51 can move towards the rotating screw 26 in the axial direction of the rotating shaft 15 between the distal end 15e of the rotating shaft 15 and the rotating screw 26. When the bushing 51 moves towards the rotating screw 26 in the axial direction of the rotating shaft 15 between the distal end 15e of the rotating shaft 15 and the rotating screw 26, the bushing flange section 53 comes into contact with the bearing flange section 58. Therefore, even when the bushing 51 moves towards the rotating screw 26 in the axial direction of the rotating shaft 15 between the distal end 15e of the rotating shaft 15 and the rotating screw 26, contact between the bushing 51 and the rotating screw 26 is prevented. This prevents a problem where the bushing 51 comes into contact with the rotating screw 26, causing abrasion between the rotating screw 26 and the bushing 51.

[0056] The groove 61 is formed in the tubular bearing section 57 and extends such that the oil is supplied from the air supply passage 46 towards the bearing flange section 58 through the groove 61. Consequently, the oil is easily supplied from the air supply passage 46 to the bearing flange section 58 through the groove 61. The cutout 62, through which the oil is supplied towards the outer circumferential edge of the bearing flange section 58, is formed in the bearing flange section 58 and is connected to the groove 61. Consequently, the oil supplied to the bearing flange section 58 through the groove 61 is easily supplied to the outer circumferential edge of the bearing flange section 58 through the cutout 62. As a consequence, even when the bushing flange section 53 comes into contact with the bearing flange section 58, there is good lubrication between the bearing flange section 58 and the bushing flange section 53. [Advantageous effect of the embodiment]

[0057] The present embodiment provides the following advantageous effects. (1) When the bushing 51 moves towards the rotating screw 26 in the axial direction of the rotating shaft 15 between the distal end 15e of the rotating shaft 15 and the rotating screw 26, the bushing flange section 53 comes into contact with the bearing flange section 58. Therefore, even when the bushing 51 moves towards the rotating screw 26 in the axial direction of the rotating shaft 15 between the distal end 15e of the rotating shaft 15 and the rotating screw 26, contact between the bushing 51 and the rotating screw 26 is prevented. This prevents the problem of the bushing 51 coming into contact with the rotating screw 26 and causing wear between the rotating screw 26 and the bushing 51.Therefore, for example, there is no need to separately provide a component for limiting the movement of the bushing 51 in the direction of the rotating worm 26 in the axial direction of the rotating shaft 15, and to separately provide a component with high abrasion resistance between the bushing 51 and the rotating worm 26 in the axial direction of the rotating shaft 15, which are different from the sliding bearing 56.

[0058] The groove 61 is formed in the tubular bearing section 57 and extends such that the oil is supplied from the air supply passage 46 towards the bearing flange section 58 through the groove 61. Consequently, the oil is easily supplied from the air supply passage 46 to the bearing flange section 58 through the groove 61. The cutout 62, through which the oil is supplied towards the outer circumferential edge of the bearing flange section 58, is formed in the bearing flange section 58 and is connected to the groove 61. Consequently, the oil supplied to the bearing flange section 58 through the groove 61 is easily supplied to the outer circumferential edge of the bearing flange section 58 through the cutout 62. As a consequence, even when the bushing flange section 53 comes into contact with the bearing flange section 58, there is good lubrication between the bearing flange section 58 and the bushing flange section 53.As described above, in the scroll compressor 10 of the present embodiment, the service life of the scroll compressor 10 is improved without increasing the number of components.

[0059] (2) The air supply passage 46 opens in a position opposite the groove 61, across the second straight line L12 in the base surface 47a of the recess 47. This increases the distance between the air supply passage 46 and the groove 61 as much as possible, so that the oil is easily supplied from the air supply passage 46 to an inner circumferential surface of the tubular bearing section 57. As a result, there is good lubrication between the tubular bearing section 57 and the tubular bushing section 52. Consequently, the service life of the scroll compressor 10 is further improved.

[0060] (3) The bearing flange section 58 is in contact with the base plate end face 26f and presses the rotating screw 26 against the stationary screw 25 and is in contact with the bushing flange section 53 and presses the bushing 51 against the distal end 15e of the rotating shaft 15. This positions the bushing 51 in the axial direction of the rotating shaft 15. Consequently, movement of the bushing 51 in the axial direction of the rotating shaft 15 between the distal end 15e of the rotating shaft 15 and the rotating screw 26 is suppressed.

[0061] (4) The bearing flange section 58 has a first extension section 59 and a second extension section 60. The first extension section 59 is arc-shaped and extends outwards from the tubular bearing section 57 in the radial direction of the rotating shaft 15, and is in contact with the bushing flange section 53. The second extension section 60 is arc-shaped and extends and inclines from the end of the first extension section 59 opposite the tubular bearing section 57 towards the base plate end face 26f, and is in contact with the base plate end face 26f. This design is suitable for positioning the bushing 51 in the axial direction of the rotating shaft 15.

[0062] (5) There is no need to provide separately the component with high abrasion resistance between the bushing 51 and the rotating screw 26 in the axial direction of the rotating shaft 15, which is different from the sliding bearing 56, so that the size of the scroll compressor 10 in the axial direction of the rotating shaft 15 can be reduced. [Modified example]

[0063] The embodiment described above can be modified as follows. The embodiment described above and the following modified examples can be combined as long as they do not contradict each other.

[0064] As in Fig. As shown in Figure 6, the first extension section 59 can be formed in an arc shape extending outwards from the tubular bearing section 57 in the radial direction of the rotating shaft 15 and can be in contact with the base plate end face 26f. The second extension section 60 can be formed in an arc shape extending and inclined from the end of the first extension section 59 opposite the tubular bearing section 57 towards the bushing flange section 53 and can be in contact with the bushing flange section 53. This design is suitable for positioning the bushing 51 in the axial direction of the rotating shaft 15.

[0065] In the embodiment, the bearing flange section 58 does not need to press the rotating screw 26 against the fixed screw 25 and does not need to press the bushing 51 against the distal end 15b of the rotating shaft 15.

[0066] In the exemplary embodiment, the air supply passage 46 can open in the bottom surface 47a of the recess 47 at a position that is closer to the groove 61 than the straight line L12.

[0067] In the exemplary embodiment, the angle of the cutout 62 between the first cutout edge 621 and the second cutout edge 622 can be an acute angle from the perspective in the axial direction of the rotating shaft 15.

[0068] In the exemplary embodiment, the cutout 62 can extend from the second extension section 60, from the perspective in the axial direction of the rotating shaft 15.

[0069] In the exemplary embodiment, the shape of the cutout 62 is not particularly restricted, as long as the cutout 62 is in contact with the groove 61 and the oil is supplied through the cutout 62 in the direction of the outer circumferential edge of the bearing flange section 58.

[0070] In this embodiment, the sliding bearing 56 does not have an annular shape and is formed by bending the strip-shaped plate material, which is made of metal; however, the sliding bearing 56 is not limited to this and can have an annular shape extending over its entire circumference. In this case, the groove 61 only needs to be formed by recessing a portion of the inner circumferential surface of the tubular bearing section 57 and extend such that the oil is supplied from the air supply passage 46 towards the bearing flange section 58 through the groove 61.

[0071] In this embodiment, the eccentric shaft 50 need not be formed integrally with the rotating shaft 15 and can be provided separately from the rotating shaft 15. In this case, the eccentric shaft 50 is attached to the distal end 15e of the rotating shaft 15.

[0072] In the exemplary embodiment, the first end of the air supply passage 46 can open in the end face of the circumferential screw base plate 26a, which is located closer to the circumferential screw spiral wall 26b, and the air supply passage 46 can be formed in the circumferential screw 26 in order to extend only through the circumferential screw base plate 26a.

[0073] In the exemplary embodiment, the counterweight 55 can be provided separately from the bushing 51.

[0074] In this embodiment, the scroll compressor 10 does not need to be driven by the motor 22 and, for example, the scroll compressor 10 can be driven by a machine of the vehicle.

[0075] In the exemplary embodiment, the scroll compressor 10 is used in the vehicle air conditioning system; however, the present invention is not limited to this. In short, the scroll compressor 10 only needs to compress the refrigerant and can be used for various applications.

[0076] In the exemplary embodiment, an object to be compressed by the scroll compressor 10 is not limited to the refrigerant and can, for example, be a fluid such as air.

[0077] A scroll compressor (10) has a housing (11), a rotating shaft (15), and a compression mechanism (C1). The rotating shaft (15) has an eccentric shaft (50). The compression mechanism (C1) has a compression chamber (27). The housing (11) has a shaft support housing (13). A refrigerant is introduced into a back-pressure chamber (45). The rotating screw (26) has an oil supply port (26). The eccentric shaft (50) is inserted into a bushing (51). The bushing (51) has a tubular bushing section (52) and a bushing flange section (53). The plain bearing (56) has a tubular bearing section (57) and a bearing flange section (58). A groove (61) is formed in the tubular bearing section (57). A cutout (62), through which the oil is supplied in the direction of an outer circumferential edge of the bearing flange section (58), is formed in the bearing flange section (58) and is connected to the groove (61). QUOTES INCLUDED IN THE DESCRIPTION

[0000] This list of documents cited by the applicant was automatically generated and is included solely for the reader's convenience. The list is not part of the German patent or utility model application. The DPMA accepts no liability for any errors or omissions. Cited patent literature

[0000] JP 2014-173436

[0007] < / ausschnitt> < / nut> < / gleitlager> < / buchse>

Claims

[1] Scroll compressor (10) with: a housing (11) which has an intake port (12h) through which a refrigerant is drawn in and a discharge port (14h) through which the refrigerant is discharged; a rotating shaft (15) which is housed in the casing (11) and is rotatably supported by the casing (11); and a compression mechanism (C1) which has a fixed screw (25) which is fixed to the housing (11) and a rotating screw (26) which rotates with a rotation of the rotating shaft (15), wherein the rotating shaft (15) has an eccentric shaft (50) projecting from a distal end (15e) of the rotating shaft (15) and extending parallel to the rotating shaft (15) at a position offset from an axial center line (L1) of the rotating shaft (15), wherein the fixed screw (25) has a fixed screw base plate (25a), a fixed screw spiral wall (25b) projecting from the fixed screw base plate (25a), and a fixed screw outer circumferential wall (25c) projecting from the fixed screw base plate (25a) and surrounding the fixed screw spiral wall (25b), wherein the rotating screw (26) has a rotating screw base plate (26a) facing the fixed screw base plate (25a) and a rotating screw spiral wall (26b) projecting from the rotating screw base plate (26a) towards the fixed screw base plate (25a) and rotating inside the fixed screw outer circumferential wall (25c), wherein the compression mechanism (C1) has a compression chamber (27) defined by the fixed screw base plate (25a), the fixed screw spiral wall (25b), the rotating screw base plate (26a) and the rotating screw spiral wall (26b) and in which the refrigerant is compressed by the engagement of the fixed screw spiral wall (25b) with the rotating screw spiral wall (26b), wherein the housing (11) has a shaft support housing (13) which is arranged on one side opposite the fixed screw base plate (25a) relative to the rotating screw base plate (26a) and supports the rotating shaft (15), wherein the refrigerant is introduced into a counter-pressure chamber (45) which is formed between a base plate end surface (26f) of the rotating screw base plate (26a) opposite the fixed screw base plate (25a) and the shaft support housing (13), wherein the refrigerant pushes the rotating screw base plate (26a) towards the fixed screw base plate (25a), wherein the rotating screw (26) has an oil supply hole (26) that opens towards the counter-pressure chamber (45) and through which oil is supplied to the counter-pressure chamber (45), wherein the eccentric shaft (50) is inserted into a bushing (51) which is pivotable around the eccentric shaft (50), wherein the base plate end surface (26f) has a recess (47) which is formed in a tubular shape with a bottom and in which the bushing (51) is arranged, wherein the recess (47) is defined by an inner circumferential surface (47b) on which a sliding bearing (56), which rotatably supports the bushing (51), is arranged, wherein the recess (47) is defined by a base surface (47a) in which the oil supply hole (46) opens, wherein the bushing (51) has a tubular bushing section (52) which is arranged inside the sliding bearing (56), and wherein the sliding bearing (56) has a tubular bearing section (57) which is arranged inside the inner circumferential surface (47a), characterized by , that the bushing (51) has a bushing flange section (53) which projects outwards from the tubular bushing section (52) in a radial direction of the rotating shaft (15), the sliding bearing (56) has a bearing flange section (58) which projects outwards in the radial direction from the tubular bearing section (57) and which is arranged between the base plate end surface (26f) and the bushing flange section (53), a groove (61) is formed in the tubular bearing section (57) and extends in such a way that the oil is supplied from the oil supply hole towards the bearing flange section (58) through the groove (61), and a cutout (62) through which the oil is supplied in the direction of an outer circumferential edge of the bearing flange section (58), in which the bearing flange section (58) is formed and is connected to the groove (61). [2] Scroll compressor (10) according to claim 1, characterized by, that, from the perspective in an axial direction of the rotating shaft (15), a straight line connecting a center (P10) of the recess (47) with the oil supply hole (46) is defined as a first straight line (L11), and a straight line passing through the center (P10) of the recess (47) and extending perpendicular to the first straight line (L11) is defined as a second straight line (L12), and the oil supply hole (46) opens in the bottom surface (47a) at a position opposite the groove (61) across the second straight line (L12). [3] Scroll compressor (10) according to claim 1 or 2, characterized by , that the bearing flange section (58) is in contact with the base plate end surface (26f) and the rotating screw (26) presses against the fixed screw (25) and is in contact with the bushing flange section (53) and the bushing (51) presses against the distal end (15e) of the rotating shaft (15). [4] Scroll compressor (10) according to claim 3, characterized by, that the bearing flange section (58) has the following: a first extension section (59) which is formed in an arc shape extending outwards from the tubular bearing section (57) in the radial direction of the rotating shaft (15), and which is in contact with the bushing flange section (53); and a second extension section (60) which is formed in an arc shape extending and inclined from one end of the first extension section (59) opposite to the tubular bearing section (57) towards the base plate end surface (26f), and which is in contact with the base plate end surface (26f). [5] Scroll compressor (10) according to claim 3, characterized by , that the bearing flange section (58) has the following: a first extension section (59) which is formed in an arc shape extending outwards from the tubular bearing section (57) in the radial direction of the rotating shaft (15), and which is in contact with the base plate end surface (26f); and a second extension section (60) which is formed in an arc shape and extends and inclines from one end of the first extension section (59) opposite from the tubular bearing section (57) to the bushing flange section (53), and which is in contact with the bushing flange section (53).

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