WO2024116464A1

WO2024116464A1 - Scroll compressor

Info

Publication number: WO2024116464A1
Application number: PCT/JP2023/027303
Authority: WO
Inventors: 海稲津; 謙並木; 裕之小林
Original assignee: 株式会社豊田自動織機
Priority date: 2022-11-29
Filing date: 2023-07-26
Publication date: 2024-06-06

Abstract

A scroll compressor (51) comprises an oil passage (60) formed on an opposing surface (51a) of a bush (51). The oil passage (60) has an inflow port (61) extending from a through-hole (54) to an outer peripheral surface of the bush (51) and opening into the outer peripheral surface of the bush (51). An oil groove (70) is formed on an inner peripheral surface of the through-hole (54) and at a portion excluding a place on which a compression load transmitted from a turning scroll acts between the inner peripheral surface of the through-hole (54) and an outer peripheral surface of an eccentric shaft (50). The oil groove (70) opens into an end surface on a turning spiral wall side in the bush (51), while being in communication with the oil passage (60).

Description

Scroll Compressor

The present invention relates to a scroll compressor.

The scroll type compressor includes a housing, a support shaft, a first scroll, and a second scroll. The support shaft is supported relative to the housing. The first scroll has a first substrate and a first spiral wall. The first spiral wall stands up from the first substrate. The second scroll has a second substrate and a second spiral wall. The second substrate faces the first substrate. The second spiral wall stands up from the second substrate toward the first substrate. The second spiral wall meshes with the first spiral wall.

The scroll compressor includes an eccentric shaft and a bush. The eccentric shaft protrudes from the tip surface of the support shaft. The eccentric shaft extends parallel to the support shaft at a position eccentric to the axis of the support shaft. The bush has a through hole into which the eccentric shaft is inserted. The bush is capable of swinging about the eccentric shaft. The scroll compressor includes a cylindrical holding portion. The holding portion is provided on the end surface of the second substrate opposite the first substrate. A bush is disposed inside the holding portion. A bearing is disposed between the inner peripheral surface of the holding portion and the outer peripheral surface of the bush. The bush is held by the holding portion via the bearing.

In order to improve the durability of scroll compressors, it is desirable to efficiently supply oil to the bearings. Therefore, for example, in Patent Document 1, a supply passage for supplying oil to the bearings is formed in the bush. The supply passage has an axial passage section extending in the axial direction of the bush and a radial passage section extending in the radial direction of the bush. The axial passage section has an inlet of the supply passage. The radial passage section has an outlet of the supply passage. Then, oil introduced from the inlet into the axial passage section flows through the axial passage section and into the radial passage section. The oil flowing through the radial passage section is supplied to the bearings via the outlet. This improves the lubrication of the bearings, thereby improving the durability of the scroll compressor.

JP 2022-83044 A

However, in Patent Document 1, in order to supply oil to the bearing, an axial flow passage portion is formed in the bush, which is a through hole separate from the through hole into which the eccentric shaft is inserted. Therefore, it is necessary to ensure that the bush has a sufficient thickness to form the axial flow passage portion, which results in the bush becoming larger. As a result, the scroll compressor becomes larger.

In order to solve the above problem, according to one aspect of the present invention, a scroll compressor is provided that includes a housing, a support shaft supported by the housing, a first scroll having a first base plate and a first spiral wall standing from the first base plate, a second base plate facing the first base plate, and a second scroll having a second spiral wall standing from the second base plate toward the first base plate and meshing with the first spiral wall, an eccentric shaft protruding from the tip surface of the support shaft and extending parallel to the support shaft at a position eccentric with respect to the axis of the support shaft, a bush having a through hole into which the eccentric shaft is inserted and capable of swinging around the eccentric shaft, a cylindrical holding portion provided on the end surface of the second base plate opposite the first base plate and with the bush disposed inside, and a bearing disposed between the inner peripheral surface of the holding portion and the outer peripheral surface of the bush. The bush is held by the holding portion via the bearing. The bush has an oil passage on the opposing surface facing the tip surface of the support shaft. The oil passage extends from the through hole toward the outer peripheral surface of the bush and has an inlet opening on the outer peripheral surface of the bush. An oil groove is formed on at least one of the inner peripheral surface of the through hole and the outer peripheral surface of the eccentric shaft, except for the portion where the compressive load transmitted from the second scroll acts between the inner peripheral surface of the through hole and the outer peripheral surface of the eccentric shaft, and communicates with the oil passage and opens on the end face of the bush on the second scroll wall side.

With this, oil present around the bush flows into the oil passage from the inlet and is supplied to the oil groove. The oil supplied to the oil groove passes through the oil groove and flows out into the space between the end face of the bush on the second volute wall side and the second base plate. The oil that flows out into this space is then supplied to the bearing. This improves the lubrication of the bearing, improving the durability of the scroll compressor.

The oil groove is formed on at least one of the inner circumferential surface of the through hole and the outer circumferential surface of the eccentric shaft. Therefore, unlike the conventional technology, there is no need to form a through hole in the bush other than the through hole into which the eccentric shaft is inserted in order to supply oil to the bearing. Therefore, there is no need to ensure the thickness of the bush. As a result, it is possible to avoid the bush becoming larger. This allows the scroll compressor to be made smaller. In addition, the oil groove is formed on at least one of the inner circumferential surface of the through hole and the outer circumferential surface of the eccentric shaft, excluding the portion where the compressive load transmitted from the second scroll acts between the inner circumferential surface of the through hole and the outer circumferential surface of the eccentric shaft. Therefore, even if the oil groove is formed on at least one of the inner circumferential surface of the through hole and the outer circumferential surface of the eccentric shaft, the rocking of the bush around the eccentric shaft is not hindered by the oil groove. As a result, the scroll compressor can be made smaller while improving its durability.

In the scroll-type compressor, the support shaft is a rotating shaft rotatably supported relative to the housing, the first scroll is a fixed scroll having a fixed base plate as the first substrate and a fixed spiral wall as the first spiral wall standing up from the fixed base plate, and the second scroll is an orbiting scroll having a rotating base plate as the second substrate facing the fixed base plate and a orbiting spiral wall as the second spiral wall standing up from the orbiting base plate toward the fixed base plate and meshing with the fixed spiral wall, and revolving with the rotation of the rotating shaft. In this way, in a scroll-type compressor equipped with a fixed scroll and an orbiting scroll, it is possible to improve durability while achieving miniaturization.

In the scroll compressor, the oil passage has a guide surface that curves from the through hole in the rotation direction of the bush when the rotating shaft is rotating in the forward direction and extends toward the inlet, and the guide surface guides the oil flowing through the oil passage toward the through hole.

As a result, the oil from the inlet is guided toward the through hole by the guide surface, making it easier for the oil from the inlet to be supplied to the oil groove via the oil passage. As a result, the oil is supplied to the bearings more efficiently, further improving the lubrication of the bearings. This can therefore further improve the durability of the scroll compressor.

In the above scroll-type compressor, the first scroll is a drive scroll having a drive substrate as the first substrate and a drive spiral wall as the first spiral wall standing up from the drive substrate, and rotating around the axis of the support shaft, and the second scroll is a driven scroll having a driven substrate as the second substrate facing the drive substrate and a driven spiral wall as the second spiral wall standing up from the driven substrate toward the drive substrate and meshing with the drive spiral wall, and rotating following the rotation of the drive scroll. In this way, in a scroll-type compressor equipped with a drive scroll and a driven scroll, it is possible to improve durability while achieving miniaturization.

In the scroll compressor, the inlet may open to a portion of an outer circumferential surface of the bush that is located vertically upward.
This allows the oil around the bush to easily fall under its own weight and flow into the inlet, so that the oil around the bush can easily flow from the inlet into the oil passage and be supplied to the oil groove, thereby improving the lubrication of the bearing and further improving the durability of the scroll compressor.

In the scroll compressor, the oil passage has a guide surface that curves from the through hole in the opposite direction to the rotation direction of the driven scroll when the drive scroll rotates in the forward direction and extends toward the inlet, and the guide surface guides the oil flowing through the oil passage toward the through hole.

Oil present around the bush flows in the rotational direction of the driven scroll, following the rotation of the driven scroll when the drive scroll rotates in the forward direction. At this time, the guide surface curves from the through hole toward the inlet in a direction opposite to the rotational direction of the driven scroll when the drive scroll rotates in the forward direction. Therefore, oil present around the bush and flowing in the rotational direction of the driven scroll is easily guided by the guide surface toward the through hole via the inlet. This makes it easier for oil from the inlet to be supplied to the oil groove via the oil passage. As a result, oil is efficiently supplied to the bearing, which further improves the lubrication of the bearing. This makes it possible to further improve the durability of the scroll compressor.

In the above scroll compressor, the outer circumferential surface of the eccentric shaft may be configured to block oil flowing through the oil passage and guide the oil to the oil groove.
According to this, the oil flowing from the inlet through the oil passage is blocked by the outer circumferential surface of the eccentric shaft and guided to the oil groove, so that the oil from the inlet is easily supplied to the oil groove through the oil passage. As a result, the oil is efficiently supplied to the bearing, and the lubrication of the bearing is further improved. Therefore, the durability of the scroll compressor can be further improved.

In the scroll compressor, the oil groove may be formed on an inner circumferential surface of the through hole.
According to this, since the oil groove is also formed in the bushing in which the oil passage is formed, it is easy to set the position of the oil groove relative to the oil passage. Therefore, the configuration in which the oil groove is formed on the inner circumferential surface of the through hole can facilitate the design of the scroll compressor.

In the scroll compressor, the oil groove may be formed in an outer circumferential surface of the eccentric shaft.
It is relatively easy to form an oil groove on the outer circumferential surface of the eccentric shaft. In this manner, a configuration in which an oil groove is formed on the outer circumferential surface of the eccentric shaft can facilitate the design of the scroll compressor.

This invention makes it possible to reduce the size of a scroll compressor while improving its durability.

FIG. 1 is a cross-sectional view of a scroll compressor according to a first embodiment. FIG. 2 is an enlarged cross-sectional view of a portion of the scroll compressor. FIG. 3 is a front view showing the bush and the eccentric shaft. FIG. 4 is a cross-sectional view showing the bush and the eccentric shaft. FIG. 5 is a cross-sectional view of a scroll compressor according to the second embodiment. FIG. 6 is an enlarged cross-sectional view showing a part of the scroll compressor. FIG. 7 is a front view showing the bush and the eccentric shaft. FIG. 8 is a cross-sectional view showing the bush and the eccentric shaft. FIG. 9 is a cross-sectional view showing a bush and an eccentric shaft in a modified example. FIG. 10 is a cross-sectional view showing a bush and an eccentric shaft in a modified example.

[First embodiment]
A scroll compressor according to a first embodiment will now be described with reference to Figures 1 to 4. The scroll compressor according to the first embodiment is used, for example, in a vehicle air conditioner.

<Basic configuration of scroll compressor 10>
As shown in Fig. 1, the scroll compressor 10 includes a cylindrical housing 11. The housing 11 includes a motor housing 12, a journal housing 13, and a discharge housing 14. The motor housing 12, the journal housing 13, and the discharge housing 14 are made of a metal material. The motor housing 12, the journal housing 13, and the discharge housing 14 are made of aluminum, for example. The scroll compressor 10 also includes a rotating shaft 15 serving as a support shaft. The rotating shaft 15 is accommodated in the housing 11.

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 coincides with the axial direction of the rotating shaft 15. The motor housing 12 has a plurality of female threaded holes 12c. Each female threaded hole 12c is formed at the open end of the peripheral wall 12b. For convenience of explanation, only one female threaded hole 12c is shown in FIG. 1. The motor housing 12 also has an intake port 12h. The intake port 12h draws in a refrigerant. The intake port 12h is formed in the peripheral wall 12b near the end wall 12a. The intake port 12h communicates between the inside and outside of the motor housing 12.

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

The journal 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 coincides with the axial direction of the rotating shaft 15. The journal housing 13 also has an annular flange wall 19. The flange wall 19 extends radially outward from the rotating shaft 15 from the end of the outer periphery of the peripheral wall 18 opposite the end wall 17.

The 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 penetrates the end wall 17 in the thickness direction. The rotating shaft 15 is inserted into the through hole 17a. The tip surface 15e located on the second end side, which is the other end in the axial direction of the rotating shaft 15, is located inside the peripheral wall 18.

The scroll compressor 10 includes a bearing 21. The bearing 21 is, for example, a rolling bearing. The bearing 21 is provided between the inner circumferential surface of the peripheral wall 18 and the outer circumferential surface of the rotating shaft 15. The rotating shaft 15 is rotatably supported by the support housing 13 via the bearing 21. In this manner, the rotating shaft 15 is rotatably supported relative to the housing 11. The support shaft in this embodiment is the rotating shaft 15 rotatably supported relative to the housing 11.

The support housing 13 has multiple 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 in the flange wall 19 is connected to each female threaded hole 12c in the motor housing 12. Note that for ease of explanation, only one bolt insertion hole 19a is shown in FIG. 1.

The scroll compressor 10 has a motor chamber 20. The motor chamber 20 is defined by the motor housing 12 and the support housing 13. The motor housing 12 defines the motor chamber 20 together with the support housing 13. In this manner, the motor chamber 20 is formed within the housing 11. The motor chamber 20 is connected to the suction port 12h. Refrigerant is drawn into the motor chamber 20 from the suction port 12h.

The scroll compressor 10 includes a motor 22. The motor 22 is housed in the 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 includes a rotor core 24a fixed to the rotating shaft 15 and a plurality of permanent magnets (not shown) provided on the rotor core 24a.

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

The scroll type compressor 10 has a compression mechanism C1. The compression mechanism C1 has a fixed scroll 25 as a first scroll, and an orbiting scroll 26 as a second scroll. Thus, the scroll type compressor 10 has a first scroll and a second scroll. The compression mechanism C1 is of a scroll type. The orbiting scroll 26 revolves around the fixed scroll 25 by the rotation of the rotating shaft 15.

The fixed scroll 25 has a fixed substrate 25a as a first substrate, and a fixed spiral wall 25b as a first spiral wall. The fixed substrate 25a is disk-shaped. A discharge port 25h is formed in the center of the fixed substrate 25a. The discharge port 25h is a circular hole. The discharge port 25h penetrates the fixed substrate 25a in the thickness direction. The fixed spiral wall 25b stands up from the fixed substrate 25a. In this way, the first scroll of this embodiment is a fixed scroll 25 having a fixed substrate 25a and a fixed spiral wall 25b. The fixed scroll 25 also has an outer peripheral wall 25c. The outer peripheral wall 25c stands up from the outer periphery of the fixed substrate 25a. The outer peripheral wall 25c surrounds the fixed spiral wall 25b.

The scroll compressor 10 is equipped with a valve mechanism 25v. The valve mechanism 25v is attached to the surface of the fixed base plate 25a opposite the fixed spiral wall 25b. The valve mechanism 25v is configured to be able to open and close the discharge port 25h.

The orbiting scroll 26 has an orbiting base plate 26a as a second base plate, and an orbiting spiral wall 26b as a second spiral wall. The orbiting base plate 26a is disk-shaped. The orbiting base plate 26a faces the fixed base plate 25a. The orbiting spiral wall 26b stands up from the orbiting base plate 26a toward the fixed base plate 25a. The orbiting spiral wall 26b meshes with the fixed spiral wall 25b. In this way, the second scroll of this embodiment is an orbiting scroll 26 having an orbiting base plate 26a and an orbiting spiral wall 26b. The orbiting scroll 26 is located inside the outer peripheral wall 25c. The orbiting scroll 26 revolves inside the outer peripheral wall 25c. The tip surface of the fixed spiral wall 25b is in contact with the orbiting base plate 26a. The tip surface of the orbiting spiral wall 26b is in contact with the fixed base plate 25a.

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

The scroll compressor 10 has a boss portion 28 as a retaining portion. The swiveling base plate 26a has a cylindrical boss portion 28. The boss portion 28 protrudes in a cylindrical shape from the end face 26e of the swiveling base plate 26a opposite the fixed base plate 25a. Therefore, the boss portion 28 is provided on the end face of the swiveling base plate 26a opposite the fixed base plate 25a. The axial direction of the boss portion 28 coincides with the axial direction of the rotating shaft 15.

The rotating base plate 26a has a plurality of grooves 26d. The grooves 26d are formed around the boss portion 28 on the end face 26e of the rotating base plate 26a. The grooves 26d are arranged at a predetermined interval in the circumferential direction of the rotating shaft 15. For the sake of explanation, only one groove 26d is shown in FIG. 1. An annular ring member 29 is fitted into each groove 26d. A pin 30 is inserted into each ring member 29. Each pin 30 protrudes from the end face 13e of the support housing 13 on the rotating scroll 26 side.

The scroll compressor 10 is equipped with an elastic plate 31. The elastic plate 31 is annular. The elastic plate 31 is sandwiched between the end face 13e of the support housing 13 and the open end face of the outer peripheral wall 25c. The elastic plate 31 constantly biases the orbiting scroll 26 toward the fixed scroll 25.

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 coincides with the axial direction of the rotating shaft 15. The peripheral wall 14b surrounds the fixed scroll 25. Therefore, the fixed scroll 25 is accommodated within the housing 11.

The discharge housing 14 has multiple bolt insertion holes 14c. Each bolt insertion hole 14c is formed in the peripheral wall 14b. For ease of explanation, only one bolt insertion hole 14c is shown in FIG. 1. Each bolt insertion hole 14c is connected to a corresponding bolt insertion hole 19a in the flange wall 19.

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

The scroll compressor 10 has 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 in a part of the inner circumferential surface of the peripheral wall 12b of the motor housing 12. The first groove 36 opens to the opening end of the peripheral wall 12b. The first hole 37 is formed in the outer circumferential portion of the flange wall 19 of the journal housing 13. The first hole 37 penetrates the flange wall 19 in the thickness direction. The first hole 37 is connected to the first groove 36. The second groove 38 is formed in a part of the inner circumferential surface of the peripheral 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 outer circumferential wall 25c of the fixed scroll 25. The second hole 39 penetrates the outer circumferential wall 25c in the thickness direction. The second hole 39 is connected to the second groove 38. The second hole 39 is connected to the outermost part of the compression chamber 27.

The refrigerant in the motor chamber 20 passes through the first groove 36, the first hole 37, the second groove 38, and the second hole 39 and is sucked into the compression chamber 27. The refrigerant sucked into the compression chamber 27 is compressed within the compression chamber 27 by the orbital motion of the orbiting scroll 26. In this way, the compression mechanism C1 compresses the refrigerant sucked into the housing 11.

The scroll compressor 10 has a discharge chamber 40. The discharge chamber 40 is defined between the fixed 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 compressed in the compression chamber 27 is discharged into the discharge chamber 40. The scroll compressor 10 also has an oil storage chamber 41. The oil storage chamber 41 is formed in the end wall 14a of the discharge housing 14.

The scroll compressor 10 has an oil separation chamber 42. The oil separation chamber 42 is formed inside the discharge housing 14. The oil separation chamber 42 is formed inside an elongated cylindrical outer cylinder 43 that is part of the end wall 14a of the discharge housing 14. The first end of the outer cylinder 43 forms a discharge port 44 that discharges the refrigerant to the outside. The discharge port 44 is connected to the oil separation chamber 42.

An inner cylinder 45 is fitted into the oil separation chamber 42. The axial direction of the inner cylinder 45 coincides with the radial direction of the rotating shaft 15. A first end of the inner cylinder 45 communicates with the discharge port 44. A second end of the inner cylinder 45 communicates with the side of the oil separation chamber 42 opposite the discharge port 44. An introduction hole 46 is formed in the outer cylinder 43. The introduction hole 46 communicates with the discharge chamber 40 and the oil separation chamber 42. The introduction hole 46 introduces the refrigerant discharged into the discharge chamber 40 into the oil separation chamber 42.

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

The refrigerant compressed in the compression chamber 27 and discharged into the discharge chamber 40 through the discharge port 25h is introduced into the oil separation chamber 42 through the introduction hole 46. The refrigerant introduced into the oil separation chamber 42 swirls around the inner cylinder 45. This applies centrifugal force to the oil contained in the refrigerant, and the oil is separated from the refrigerant in the oil separation chamber 42. Therefore, the oil separation chamber 42 separates the oil contained in the refrigerant discharged into the discharge chamber 40.

The refrigerant from which the oil has been separated flows into and passes through the inner cylinder 45. The refrigerant that has passed through the inner cylinder 45 flows out through the discharge port 44 to an external refrigerant circuit (not shown). The oil separated from the refrigerant in the oil separation chamber 42 flows toward the oil drain hole 47. The oil flowing toward the oil drain hole 47 is discharged through the oil drain hole 47 into the oil storage chamber 41 and is stored in the oil storage chamber 41.

The scroll compressor 10 is equipped with an oil return passage 48. The oil return passage 48 passes from the oil storage chamber 41 through the discharge housing 14 and the support housing 13 to the inside of the peripheral wall 18 of the support housing 13. Therefore, the oil return passage 48 connects the oil storage chamber 41 to the inside of the peripheral wall 18 of the support housing 13. The oil stored in the oil storage chamber 41 is returned to the inside of the peripheral wall 18 of the support housing 13 via the oil return passage 48.

The scroll compressor 10 is equipped with an eccentric shaft 50. The eccentric shaft 50 protrudes from the tip surface 15e of the rotating shaft 15 and extends parallel to the rotating shaft 15 at a position eccentric with respect to the axis L1 of the rotating shaft 15. The eccentric shaft 50 is integrally formed 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 protrudes from the tip surface 15e of the rotating shaft 15 toward the orbiting scroll 26. The eccentric shaft 50 is inserted into the boss portion 28.

<Bush 51>
As shown in Fig. 2, the scroll compressor 10 includes a bush 51. The bush 51 has a bush cylindrical portion 52 and a bush flange portion 53. The inside of the bush cylindrical portion 52 is formed as a through hole 54. Therefore, the bush 51 has the through hole 54. The eccentric shaft 50 is inserted into the through hole 54. The bush cylindrical portion 52 is disposed inside the boss portion 28. Therefore, the bush 51 is disposed inside the boss portion 28.

The end of the bushing cylinder 52 opposite the swivel base plate 26a protrudes from the boss 28. The bushing flange 53 protrudes outward in a ring shape from the end of the bushing cylinder 52 opposite the swivel base plate 26a. The bushing flange 53 overlaps with the end face of the boss 28 in the axial direction of the boss 28. The bushing 51 can swing around the eccentric shaft 50.

The scroll compressor 10 is equipped with a balance weight 55. The balance weight 55 is integrated with the bush 51. The balance weight 55 is formed integrally with the bush 51. The balance weight 55 protrudes outward from a portion of the outer circumferential surface of the bush flange portion 53. The balance weight 55 is housed within the peripheral wall 18 of the support housing 13.

<Bearing 56>
The scroll compressor 10 includes a bearing 56. The bearing 56 is a cylindrical sliding bearing. The bearing 56 has a bearing tube portion 57 and a bearing flange portion 58. The bearing tube portion 57 is disposed inside the boss portion 28. The bearing tube portion 57 is disposed between the inner peripheral surface of the boss portion 28 and the outer peripheral surface of the bushing tube portion 52. Therefore, the bearing 56 is disposed between the inner peripheral surface of the boss portion 28 and the outer peripheral surface of the bushing 51. The bushing 51 is rotatably held by the boss portion 28 via the bearing 56.

The end of the bearing tube 57 opposite the swivel base plate 26a protrudes from the boss 28. The bearing flange 58 protrudes outward in an annular shape from the end of the bearing tube 57 opposite the swivel base plate 26a. The bearing flange 58 is disposed between the end face of the boss 28 and the bush flange 53. The bearing 56 is prevented from coming loose from the boss 28 by the bearing flange 58 abutting against the bush flange 53.

The rotation of the rotating shaft 15 is transmitted to the orbiting scroll 26 via the eccentric shaft 50, the bush 51, and the bearing 56. This causes the orbiting scroll 26 to rotate on its axis. Then, the contact between each pin 30 and the inner peripheral surface of each ring member 29 prevents the orbiting scroll 26 from rotating on its axis, and only the revolution of the orbiting scroll 26 is permitted. As a result, the orbiting scroll 26 revolves while the orbiting spiral wall 26b is in contact with the fixed spiral wall 25b. As the orbiting scroll 26 revolves, the volume of the compression chamber 27 decreases, and the refrigerant is compressed in the compression chamber 27. The orbiting scroll 26 revolves inside the outer peripheral wall 25c as the rotating shaft 15 rotates. The balance weight 55 offsets the centrifugal force acting on the orbiting scroll 26 when it revolves. This reduces the amount of imbalance in the orbiting scroll 26.

<Follower crank mechanism 59>
The center L2 of the bushing cylindrical portion 52 is located radially outward of the axis L1 of the rotating shaft 15. The center of the orbiting base plate 26a coincides with the center L2 of the bushing cylindrical portion 52. The distance between the center L2 of the bushing cylindrical portion 52 and the axis L1 of the rotating shaft 15 is the orbital radius of the orbiting scroll 26.

When the bush 51 swings around the eccentric shaft 50, the distance between the center L2 of the bush 51 and the axis L1 of the rotating shaft 15 changes, and the orbital radius of the orbiting scroll 26 becomes variable. In this way, the eccentric shaft 50, the bush 51, and the bearing 56 constitute a so-called driven crank mechanism 59 that changes the orbital radius of the orbiting scroll 26. Such a driven crank mechanism 59 is already known.

As shown in FIG. 3, the through hole 54 has a center L3 that is eccentric to the center L2 of the bushing cylindrical portion 52. Therefore, in the bushing cylindrical portion 52, the thickness of the portion closer to the center L3 of the through hole 54 than the center L2 of the bushing cylindrical portion 52 is smaller than the thickness of the portion closer to the center L2 of the bushing cylindrical portion 52 than the center L3 of the through hole 54.

<Compressive load F1>
A compressive load F1 is applied from the orbiting scroll 26 between the inner peripheral surface of the through hole 54 and the outer peripheral surface of the eccentric shaft 50. The compressive load F1 is applied from the orbiting scroll 26 to the eccentric shaft 50 via the bearing 56 and the bush 51. The compressive load F1 is uniquely determined by the shapes of the fixed spiral wall 25b and the orbiting spiral wall 26b, the pressure of the refrigerant compressed in the compression chamber 27, and the like. A location A1 where the compressive load F1 transmitted from the orbiting scroll 26 acts between the inner peripheral surface of the through hole 54 and the outer peripheral surface of the eccentric shaft 50 is grasped in advance by experiments, etc. In this embodiment, the compressive load F1 is applied to the eccentric shaft 50 from a portion of the bushing cylindrical portion 52 that is closer to the center L3 of the through hole 54 than the center L2 of the bushing cylindrical portion 52.

<Function of the driven crank mechanism 59>
Since minute machining errors and assembly errors occur in the fixed scroll 25 and the orbiting scroll 26, a play (gap) is provided in advance between the fixed spiral wall 25b and the orbiting spiral wall 26b.

When the rotating shaft 15 rotates in the forward direction, the bush 51 oscillates around the eccentric shaft 50 based on the compressive load F1 acting on the orbiting scroll 26. When the bush 51 oscillates around the eccentric shaft 50, the distance between the center L2 of the bush 51 and the axis L1 of the rotating shaft 15 increases, and the orbital radius of the orbiting scroll 26 increases. Then, when the orbiting spiral wall 26b comes into contact with the fixed spiral wall 25b, the oscillation of the bush 51 around the eccentric shaft 50 is restricted. This fixes the orbital radius of the orbiting scroll 26.

Furthermore, the rotation of the rotating shaft 15 is transmitted to the orbiting scroll 26 via the eccentric shaft 50, the bush 51, and the bearing 56, so that the orbiting scroll 26 rotates in the forward direction. Then, when the orbiting spiral wall 26b comes into contact with the fixed spiral wall 25b, the pin 30 comes into contact with the ring member 29. This prevents the orbiting scroll 26 from rotating on its axis, and only allows the orbiting scroll 26 to revolve in the forward direction. Then, the orbiting scroll 26 revolves in the forward direction while the orbiting spiral wall 26b comes into contact with the fixed spiral wall 25b. This prevents the refrigerant from leaking from the compression chamber 27, and the volume of the compression chamber 27 decreases, compressing the refrigerant.

When assembling the orbiting scroll 26 to the fixed scroll 25, the bush 51 is swung around the eccentric shaft 50 in the opposite direction to when the rotating shaft 15 is rotating in the forward direction. This reduces the distance between the center L2 of the bush 51 and the axis L1 of the rotating shaft 15, thereby reducing the orbital radius of the orbiting scroll 26. As a result, the position of the orbiting spiral wall 26b relative to the fixed spiral wall 25b becomes a position where the orbiting spiral wall 26b does not come into contact with the fixed spiral wall 25b. This makes it possible to easily assemble the orbiting scroll 26 to the fixed scroll 25.

When the bush 51 oscillates around the eccentric shaft 50 in the opposite direction to when the rotating shaft 15 is rotating in the forward direction, the bush 51 is restricted from oscillating until the distance between the center L2 of the bush 51 and the axis L1 of the rotating shaft 15 increases. When the bush 51 oscillates around the eccentric shaft 50 in the opposite direction to when the rotating shaft 15 is rotating in the forward direction, the bush 51 is restricted from oscillating when the distance between the center L2 of the bush 51 and the axis L1 of the rotating shaft 15 becomes the shortest distance.

<Oil passage 60>
2, the bush 51 has an oil passage 60. The oil passage 60 is formed in an opposing surface 51a of the bush 51 that faces the tip surface 15e of the rotary shaft 15.

As shown in FIG. 4, the oil passage 60 extends from the through hole 54 toward the outer peripheral surface of the bush flange 53. Therefore, the oil passage 60 extends from the through hole 54 toward the outer peripheral surface of the bush 51. The oil passage 60 has an inlet 61 that opens into the outer peripheral surface of the bush flange 53. Therefore, the oil passage 60 has an inlet 61 that opens into the outer peripheral surface of the bush 51. A first end of the oil passage 60 is the inlet 61 that opens into the outer peripheral surface of the bush 51. A second end of the oil passage 60 is connected to the through hole 54.

The oil passage 60 is defined by a passage forming recess 62 formed in the opposing surface 51a. The passage forming recess 62 has a bottom surface 63 and a first side surface 64 and a second side surface 65 standing upright from the bottom surface 63. The bottom surface 63 connects the first side surface 64 and the second side surface 65 to each other. The bottom surface 63 is continuous with the through hole 54. The bottom surface 63 extends from the through hole 54 toward the outer peripheral surface of the bush flange portion 53.

In FIG. 4, the direction of rotation of the bush 51 when the rotating shaft 15 is rotating in the positive direction is indicated by arrow R1. The first side 64 is located further ahead of the second side 65 in the direction of rotation of the bush 51 when the rotating shaft 15 is rotating in the positive direction. The first side 64 and the second side 65 extend from the outer circumferential surface of the eccentric shaft 50 toward the outer circumferential surface of the bush flange portion 53.

The first side surface 64 and the second side surface 65 are curved from the outer circumferential surface of the eccentric shaft 50 in the rotation direction of the bush 51 when the rotating shaft 15 is rotating in the positive direction. Therefore, the first side surface 64 and the second side surface 65 each have a guide surface 66 that curves from the through hole 54 in the rotation direction of the bush 51 when the rotating shaft 15 is rotating in the positive direction and extends toward the inlet 61. Therefore, the oil passage 60 has a guide surface 66 that curves from the through hole 54 in the rotation direction of the bush 51 when the rotating shaft 15 is rotating in the positive direction and extends toward the inlet 61. Each guide surface 66 guides the oil flowing through the oil passage 60 toward the through hole 54.

<Oil groove 70>
As shown in FIG. 3, an oil groove 70 is formed on the inner circumferential surface of the through hole 54. The oil groove 70 is formed on the inner circumferential surface of the through hole 54. The oil groove 70 is formed on the inner circumferential surface of the through hole 54 at a portion closer to the center L2 of the bushing cylindrical portion 52 than the center L3 of the through hole 54. The oil groove 70 is formed on the inner circumferential surface of the through hole 54 at a portion that is out of phase with the portion on which the compressive load F1 transmitted from the orbiting scroll 26 acts between the inner circumferential surface of the through hole 54 and the outer circumferential surface of the eccentric shaft 50. The oil groove 70 is formed on the inner circumferential surface of the through hole 54 at a portion excluding the portion on which the compressive load F1 transmitted from the orbiting scroll 26 acts between the inner circumferential surface of the through hole 54 and the outer circumferential surface of the eccentric shaft 50.

As shown in FIG. 2, the first end of the oil groove 70 is connected to the second end of the oil passage 60. The second end of the oil groove 70 opens to the end face of the bush 51 on the side of the swirling volute wall 26b. The oil groove 70 connects the second end of the oil passage 60 to the space 71 between the end face of the bush 51 on the side of the swirling volute wall 26b and the swirling base plate 26a.

As shown in FIG. 4, the outer peripheral surface of the eccentric shaft 50 blocks the second end of the oil passage 60. The outer peripheral surface of the eccentric shaft 50 blocks the oil flowing through the oil passage 60 and guides it to the oil groove 70.

[Operation of the First Embodiment]
Next, the operation of the first embodiment will be described.
Within the peripheral wall 18 of the bearing housing 13, the oil stored in the oil reservoir 41 is returned via the oil return passage 48. Then, the oil present around the outer circumferential surface of the bush 51 flows from the inlet 61 into the oil passage 60 and is supplied to the oil groove 70. At this time, the oil from the inlet 61 is guided toward the through hole 54 by the guide surface 66, so that the oil from the inlet 61 is easily supplied to the oil groove 70 via the oil passage 60. Also, the oil flowing through the oil passage 60 from the inlet 61 is blocked by the outer circumferential surface of the eccentric shaft 50 and guided to the oil groove 70, so that the oil from the inlet 61 is easily supplied to the oil groove 70 via the oil passage 60.

Oil supplied to oil groove 70 passes through oil groove 70 and flows out into space 71 between the end face of bush 51 facing swivel base plate 26a and swivel base plate 26a. The oil that flows out into space 71 is then supplied to bearing 56. This ensures good lubrication of bearing 56.

[Effects of the First Embodiment]
The first embodiment can provide the following effects.
(1-1) The bush 51 has an oil passage 60 on the facing surface 51a facing the tip surface 15e of the rotating shaft 15. The oil passage 60 extends from the through hole 54 toward the outer circumferential surface of the bush 51 and has an inlet 61 that opens on the outer circumferential surface of the bush 51. An oil groove 70 is formed on the inner circumferential surface of the through hole 54, except for the portion where the compression load F1 transmitted from the orbiting scroll 26 acts between the inner circumferential surface of the through hole 54 and the outer circumferential surface of the eccentric shaft 50. The oil groove 70 communicates with the oil passage 60 and opens on the end surface of the bush 51 on the orbiting scroll wall 26b side. According to this, the oil present around the bush 51 flows into the oil passage 60 from the inlet 61 and is supplied to the oil groove 70. The oil supplied to the oil groove 70 passes through the oil groove 70 and flows out into the space 71 between the end surface of the bush 51 on the orbiting scroll wall 26b side and the orbiting base plate 26a. The oil that has flowed out into the space 71 is supplied to the bearing 56. This improves the lubrication of the bearing 56, thereby improving the durability of the scroll compressor 10.

The oil groove 70 is formed on the inner peripheral surface of the through hole 54. Therefore, unlike the conventional technology, there is no need to form a through hole in the bush 51 other than the through hole 54 into which the eccentric shaft 50 is inserted in order to supply oil to the bearing 56. Therefore, there is no need to ensure the thickness of the bush 51. As a result, it is possible to avoid the bush 51 becoming larger. Therefore, it is possible to reduce the size of the scroll compressor 10. In addition, the oil groove 70 is formed on the inner peripheral surface of the through hole 54, and in a portion excluding the portion where the compression load F1 transmitted from the orbiting scroll 26 acts between the inner peripheral surface of the through hole 54 and the outer peripheral surface of the eccentric shaft 50. Therefore, even if the oil groove 70 is formed on the inner peripheral surface of the through hole 54, the rocking motion of the bush 51 around the eccentric shaft 50 is not hindered by the oil groove 70. As a result, it is possible to improve the durability while reducing the size of the scroll compressor 10.

(1-2) In this way, in the scroll-type compressor 10 having the fixed scroll 25 and the orbiting scroll 26, it is possible to reduce the size and improve the durability.
(1-3) The oil passage 60 has a guide surface 66 that curves in the rotation direction of the bush 51 when the rotating shaft 15 rotates in the forward direction from the through hole 54 and extends toward the inlet 61. The guide surface 66 guides the oil flowing through the oil passage 60 toward the through hole 54. With this, the oil from the inlet 61 is guided toward the through hole 54 by the guide surface 66, so that the oil from the inlet 61 is easily supplied to the oil groove 70 via the oil passage 60. As a result, the oil is efficiently supplied to the bearing 56, and the lubrication of the bearing 56 is further improved. Therefore, the durability of the scroll compressor 10 can be further improved.

(1-4) The outer peripheral surface of the eccentric shaft 50 blocks the oil flowing through the oil passage 60 and guides it to the oil groove 70. As a result, the oil flowing through the oil passage 60 from the inlet 61 is blocked by the outer peripheral surface of the eccentric shaft 50 and guided to the oil groove 70. This makes it easier for the oil from the inlet 61 to be supplied to the oil groove 70 via the oil passage 60. As a result, oil is efficiently supplied to the bearing 56, which further improves the lubrication of the bearing 56. This further improves the durability of the scroll compressor 10.

(1-5) The oil groove 70 is formed on the inner circumferential surface of the through hole 54. With this, since the oil groove 70 is also formed in the bush 51 in which the oil passage 60 is formed, it is easy to set the position of the oil groove 70 relative to the oil passage 60. Therefore, a configuration in which the oil groove 70 is formed on the inner circumferential surface of the through hole 54 can facilitate the design of the scroll compressor 10.

[Second embodiment]
A second embodiment of a scroll compressor will be described below with reference to Figures 5 to 8. In the embodiment described below, the same components as those in the first embodiment are denoted by the same reference numerals, and redundant description will be omitted or simplified. The scroll compressor of the second embodiment is a double-rotating scroll compressor.

<Basic configuration of scroll compressor 100>
As shown in Fig. 5, the scroll compressor 100 includes a housing 101. The housing 101 includes a housing body 102 and a housing cover 103. The housing body 102 and the housing cover 103 are made of a metal material. The housing body 102 and the housing cover 103 are made of aluminum, for example.

The housing body 102 has a disk-shaped end wall 102a and a cylindrical peripheral wall 102b. The peripheral wall 102b extends from the outer periphery of the end wall 102a. The housing body 102 has an intake port 104. The intake port 104 draws in a refrigerant. The intake port 104 is formed, for example, in the end wall 102a. The intake port 104 connects the inside and outside of the housing body 102.

The scroll compressor 100 is equipped with a support shaft 105. The support shaft 105 is provided in the housing body 102. Therefore, the support shaft 105 is supported relative to the housing 101. The support shaft 105 protrudes from the center of the inner surface of the end wall 102a of the housing body 102. The axis L11 of the support shaft 105 coincides with the axis of the peripheral wall 102b of the housing body 102. The support shaft 105 is formed integrally with the housing body 102.

The housing cover 103 is plate-shaped. The housing cover 103 is connected to the end of the peripheral wall 102b of the housing body 102 opposite the end wall 102a. The housing cover 103 is connected to the housing body 102 while closing the opening of the peripheral wall 102b. The housing body 102 and the housing cover 103 define a scroll chamber 106. The housing 101 therefore defines the scroll chamber 106. Refrigerant is drawn into the scroll chamber 106 from the suction port 104.

The housing cover 103 has a bearing retaining portion 107. The bearing retaining portion 107 is cylindrical and protrudes from the center of the inner surface of the housing cover 103. The axis of the bearing retaining portion 107 coincides with the axis of the peripheral wall 102b of the housing body 102. The bearing retaining portion 107 retains a bearing 108. The bearing 108 is, for example, a needle bearing. The housing cover 103 has a discharge hole 109. The discharge hole 109 passes through the center of the housing cover 103. The discharge hole 109 is connected to the inside of the bearing retaining portion 107.

The scroll compressor 100 includes a motor 110. The motor 110 is housed in the scroll chamber 106. Therefore, the scroll chamber 106 also serves as a motor chamber in which the motor 110 is housed. The motor 110 includes a cylindrical stator 111 and a cylindrical rotor 112. The stator 111 includes a cylindrical stator core 113 and a motor coil 114. The stator core 113 is fixed to the inner circumferential surface of the peripheral wall 102b of the housing body 102. The motor coil 114 is wound around the stator core 113. The rotor 112 is disposed inside the stator 111. The rotor 112 includes a cylindrical rotor core 115 and a plurality of permanent magnets (not shown) provided in the rotor core 115.

The scroll type compressor 100 includes a compression mechanism 116. The compression mechanism 116 is housed in the scroll chamber 106. The compression mechanism 116 includes a driving scroll 117 as a first scroll, and a driven scroll 118 as a second scroll. The compression mechanism 116 is of a scroll type. The driven scroll 118 rotates following the rotation of the driving scroll 117.

The driving scroll 117 has a driving substrate 117a as a first substrate, and a driving spiral wall 117b as a first spiral wall. The driving substrate 117a is disk-shaped. A discharge port 119 is formed in the center of the driving substrate 117a. The discharge port 119 is a circular hole. The discharge port 119 penetrates the driving substrate 117a in the thickness direction. The driving spiral wall 117b stands upright from the driving substrate 117a. In this way, the first scroll of this embodiment is a driving scroll having a driving substrate 117a and a driving spiral wall 117b.

The outer periphery of the surface of the drive substrate 117a that faces the drive spiral wall 117b is in contact with the first end face of the rotor core 115. The drive spiral wall 117b is located inside the rotor core 115. Therefore, the rotor core 115 surrounds the drive spiral wall 117b.

The driving scroll 117 has a first boss portion 120. The first boss portion 120 protrudes from the center of the surface of the driving substrate 117a located on the opposite side to the driving spiral wall 117b. The first boss portion 120 is cylindrical. The driving scroll 117 is accommodated in the scroll chamber 106 with the axis of the first boss portion 120 coinciding with the axis L11 of the support shaft 105. The inside of the first boss portion 120 communicates with the discharge port 119. The first boss portion 120 fits into the inside of the bearing holder 107. The first boss portion 120 is rotatably supported by the bearing holder 107 via the bearing 108.

The driving scroll 117 has a driving cover body 121. The driving cover body 121 has a disk-shaped cover end wall 121a and a cylindrical cover peripheral wall 121b. The cover peripheral wall 121b extends from the outer periphery of the cover end wall 121a. The driving cover body 121 is accommodated in the scroll chamber 106 with the axis of the cover peripheral wall 121b coinciding with the axis L11 of the support shaft 105.

The inner diameter of the cover peripheral wall 121b is the same as the inner diameter of the rotor core 115. The end face located on the opening side of the cover peripheral wall 121b abuts against the second end face of the rotor core 115 with the inner peripheral surface of the cover peripheral wall 121b and the inner peripheral surface of the rotor core 115 located on the same plane. The cover peripheral wall 121b and the drive board 117a sandwich the rotor core 115. The drive board 117a, the rotor core 115, and the cover peripheral wall 121b are connected by a plurality of bolts 122. Therefore, the drive scroll 117 is integrated with the rotor 112. The drive scroll 117 can rotate integrally with the rotor 112.

The drive cover body 121 has a second boss portion 123. The second boss portion 123 protrudes from the center of the surface of the cover end wall 121a located opposite the cover peripheral wall 121b. The second boss portion 123 is cylindrical. The axis of the second boss portion 123 coincides with the axis of the cover peripheral wall 121b. The cover end wall 121a has an insertion hole 124. The insertion hole 124 penetrates the cover end wall 121a in the thickness direction. The insertion hole 124 communicates with the inside of the second boss portion 123. The hole diameter of the insertion hole 124 is the same as the inner diameter of the second boss portion 123. The inner peripheral surface of the insertion hole 124 and the inner peripheral surface of the second boss portion 123 are located on the same plane.

The support shaft 105 is inserted inside the second boss portion 123 and into the insertion hole 124. A bearing 125 is provided between the support shaft 105 and the second boss portion 123 and the insertion hole 124. The bearing 125 is, for example, a sliding bearing. The drive cover body 121 is supported rotatably relative to the support shaft 105 via the bearing 125. In this way, the drive scroll 117 rotates around the axis L11 of the support shaft 105.

The drive cover body 121 has a plurality of grooves 126. The grooves 126 are formed on the surface of the cover end wall 121a that faces the cover peripheral wall 121b. Each groove 126 is a circular recess. The grooves 126 are arranged around the insertion hole 124 at predetermined intervals in the circumferential direction of the cover peripheral wall 121b. An annular ring member 127 is fitted into each groove 126.

The drive cover body 121 has a suction port 121h. The suction port 121h is formed on the outer periphery of the cover end wall 121a. The suction port 121h draws the refrigerant drawn into the scroll chamber 106 from the suction port 104 into the inside of the cover peripheral wall 121b.

The scroll compressor 100 is equipped with a valve mechanism 128. The valve mechanism 128 is attached to the surface of the drive substrate 117a that is located on the opposite side to the drive volute wall 117b. The valve mechanism 128 is configured to be able to open and close the discharge port 119.

The driven scroll 118 has a driven substrate 118a as a second substrate, and a driven spiral wall 118b as a second spiral wall. The driven substrate 118a is disk-shaped. The driven substrate 118a faces the driving substrate 117a. The driven spiral wall 118b stands up from the driven substrate 118a toward the driving substrate 117a. The driven spiral wall 118b is engaged with the driving spiral wall 117b. In this way, the second scroll of this embodiment is a driven scroll 118 having a driven substrate 118a and a driven spiral wall 118b.

The driven scroll 118 is disposed inside the cover peripheral wall 121b and the rotor core 115. The tip surface of the driving spiral wall 117b is in contact with the driven substrate 118a. The tip surface of the driving spiral wall 118b is in contact with the driving substrate 117a.

The scroll compressor 100 has a compression chamber 129. The compression chamber 129 is defined by the drive base plate 117a, the drive spiral wall 117b, the driven base plate 118a, and the driven spiral wall 118b. Thus, the compression chamber 129 is defined between the drive scroll 117 and the driven scroll 118. The compression chamber 129 takes in and compresses the refrigerant from the suction port 121h.

The scroll compressor 100 is provided with a holding portion 130. The holding portion 130 is formed on the driven substrate 118a. The holding portion 130 is a circular hole-shaped recess formed in the center of the surface of the driven substrate 118a located opposite the driven spiral wall 118b. Therefore, the holding portion 130 is cylindrical and provided on the end surface of the driven substrate 118a opposite the drive substrate 117a. A plurality of pins 131 protrude from the end surface of the driven substrate 118a opposite the drive substrate 117a. Each pin 131 is inserted into each ring member 127.

As shown in FIG. 6, the scroll compressor 100 is equipped with an eccentric shaft 132. The eccentric shaft 132 protrudes from the tip surface 105a of the support shaft 105. The eccentric shaft 132 extends parallel to the support shaft 105 at a position eccentric with respect to the axis L11 of the support shaft 105. The eccentric shaft 132 is fixed to the support shaft 105 by being pressed into a press-fit hole 105h formed in the tip surface 105a of the support shaft 105. The eccentric shaft 132 is inserted inside the retaining portion 130.

<Bush 133>
The scroll compressor 100 includes a bush 133. The bush 133 is cylindrical. The inside of the bush 133 is formed with a through hole 134. Therefore, the bush 133 has the through hole 134. The eccentric shaft 132 is inserted into the through hole 134. The bush 133 is disposed inside the holding portion 130. Therefore, the bush 133 is disposed inside the holding portion 130. The bush 133 can oscillate (swing) around the eccentric shaft 132.

<Bearing 135>
The scroll compressor 100 includes a bearing 135. The bearing 135 is disposed inside the holding portion 130. The bearing 135 is disposed between an inner peripheral surface of the holding portion 130 and an outer peripheral surface of the bush 133. The bush 133 is held by the holding portion 130 via the bearing 135.

<Operations of the driving scroll 117 and the driven scroll 118>
5, in the scroll compressor 100, the rotor 112 rotates when power controlled by an inverter (not shown) is supplied to the motor coil 114. Then, in conjunction with the rotation of the rotor 112, the driving scroll 117 rotates about the axis L11 of the support shaft 105. The rotation of the driving scroll 117 is transmitted to the driven scroll 118 by the sliding contact between each pin 131 and each ring member 127.

As shown in FIG. 6, the driven scroll 118 rotates around the center L12 of the bush 133. At this time, the contact between each pin 131 and each ring member 127 causes the driven scroll 118 to revolve relative to the driving scroll 117. As a result, the driven scroll 118 rotates with the driven spiral wall 118b in contact with the driving spiral wall 117b. In this way, the driven scroll 118 rotates following the rotation of the driving scroll 117. Then, with the rotation of the driving scroll 117 and the driven scroll 118, the volume of the compression chamber 129 decreases, and the refrigerant is compressed in the compression chamber 129.

The center L12 of the bushing 133 is located radially outward of the axis L11 of the support shaft 105. The center of the driven base plate 118a coincides with the center L12 of the bushing 133. The distance between the center L12 of the bushing 133 and the axis L11 of the support shaft 105 is the orbital radius of the driven scroll 118, which revolves relative to the driving scroll 117.

As the bush 133 swings around the eccentric shaft 132, the distance between the center L12 of the bush 133 and the axis L11 of the support shaft 105 changes. In this way, the eccentric shaft 132, the bush 133, and the bearing 135 constitute a so-called driven crank mechanism 136 that varies the distance between the center L12 of the bush 133 and the axis L11 of the support shaft 105. Such a driven crank mechanism 136 is already known.

As shown in FIG. 7, the through hole 134 has a center L13 at a position eccentric to the center L12 of the bush 133. Therefore, in the bush 133, the thickness of the portion closer to the center L13 of the through hole 134 than the center L12 of the bush 133 is smaller than the thickness of the portion closer to the center L12 of the bush 133 than the center L13 of the through hole 134.

<Compressive load F1>
A compressive load F1 is applied between the inner peripheral surface of the through hole 134 and the outer peripheral surface of the eccentric shaft 132 from the driven scroll 118. The compressive load F1 is applied to the eccentric shaft 132 from the driven scroll 118 via the bearing 108 and the bush 133. The compressive load F1 is uniquely determined by the shapes of the driving spiral wall 117b and the driven spiral wall 118b, the pressure of the refrigerant compressed in the compression chamber 129, and the like. Furthermore, the compressive load F1 is uniquely determined by the eccentric direction of the eccentric shaft 132 with respect to the axis L11 of the support shaft 105. A location A1 where the compressive load F1 transmitted from the driven scroll 118 acts between the inner peripheral surface of the through hole 134 and the outer peripheral surface of the eccentric shaft 132 is grasped in advance by experiments, etc. In this embodiment, the compressive load F1 is applied to the eccentric shaft 132 from a portion of the bush 133 closer to the center L13 of the through hole 134 than the center L12 of the bush 133.

<Function of the driven crank mechanism 136>
Since minute processing errors and assembly errors occur in the driving scroll 117 and the driven scroll 118, a play (gap) is provided in advance between the driving spiral wall 117b and the driven spiral wall 118b.

When the driving scroll 117 rotates in the forward direction, the driven scroll 118 follows and rotates in the forward direction. Then, the bush 133 oscillates around the eccentric shaft 132 based on the compressive load F1 acting on the driven scroll 118. When the bush 133 oscillates around the eccentric shaft 132, the distance between the center L12 of the bush 133 and the axis L11 of the support shaft 105 increases. Then, when the driven spiral wall 118b comes into contact with the driving spiral wall 117b, the oscillation of the bush 133 around the eccentric shaft 132 is restricted. This fixes the distance between the center L12 of the bush 133 and the axis L11 of the support shaft 105.

When assembling the driven scroll 118 to the driving scroll 117, the bush 133 is swung around the eccentric shaft 132 in the opposite direction to when the driving scroll 117 is rotating in the forward direction. This reduces the distance between the center L12 of the bush 133 and the axis L11 of the support shaft 105. This causes the position of the driven spiral wall 118b relative to the driving spiral wall 117b to be such that the driven spiral wall 118b does not come into contact with the driving spiral wall 117b. This makes it possible to easily assemble the driven scroll 118 to the driving scroll 117.

When the bush 133 oscillates around the eccentric shaft 132 in the opposite direction to when the drive scroll 117 is rotating in the forward direction, the bush 133 is restricted from oscillating until the distance between the center L12 of the bush 133 and the axis L11 of the support shaft 105 increases. When the bush 133 oscillates around the eccentric shaft 132 in the opposite direction to when the drive scroll 117 is rotating in the forward direction, the bush 133 is restricted from oscillating when the distance between the center L12 of the bush 133 and the axis L11 of the support shaft 105 becomes the shortest distance.

<Oil passage 137>
6, the bushing 133 has an oil passage 137. The oil passage 137 is formed in an opposing surface 133a of the bushing 133 that faces the tip end surface 105a of the support shaft 105.

As shown in FIG. 8, the oil passage 137 extends from the through hole 134 toward the outer peripheral surface of the bush 133. The oil passage 137 has an inlet 139 that opens into the outer peripheral surface of the bush 133. A first end of the oil passage 137 is the inlet 139 that opens into the outer peripheral surface of the bush 133. A second end of the oil passage 137 is connected to the through hole 134.

The inlet 139 opens at a portion of the outer circumferential surface of the bush 133 that is located above the vertical direction Z1. The inlet 139 opens at a portion of the outer circumferential surface of the bush 133 that is located above the vertical direction Z1 of an imaginary plane 140 that passes horizontally through the center L12 of the bush 133. The bush 133 is held by the holding portion 130 so that the inlet 139 opens at a portion of the outer circumferential surface of the bush 133 that is located above the vertical direction Z1 when the oscillation of the bush 133 about the eccentric shaft 132 is restricted.

The oil passage 137 is defined by a passage forming recess 141 formed in the opposing surface 133a. The passage forming recess 141 has a bottom surface 142 and a first side surface 143 and a second side surface 144 standing upright from the bottom surface 142. The bottom surface 142 connects the first side surface 143 and the second side surface 144 to each other. The bottom surface 142 is continuous with the through hole 134. The bottom surface 142 extends from the through hole 134 toward the outer peripheral surface of the bush 133.

In FIG. 8, the direction of rotation of the driven scroll 118 when the driving scroll 117 is rotating in the forward direction is indicated by arrow R2. The first side surface 143 is located on the leading side of the second side surface 144 in the direction of rotation of the driven scroll 118 when the driving scroll 117 is rotating in the forward direction. The first side surface 143 and the second side surface 144 extend from the outer circumferential surface of the eccentric shaft 132 toward the outer circumferential surface of the bush 133.

The first side surface 143 and the second side surface 144 are curved in the opposite direction to the rotation direction of the driven scroll 118 when the driving scroll 117 rotates in the forward direction from the outer peripheral surface of the eccentric shaft 132. Therefore, the first side surface 143 and the second side surface 144 each have a guide surface 145 that curves in the opposite direction to the rotation direction of the driven scroll 118 when the driving scroll 117 rotates in the forward direction from the through hole 134 and extends toward the inlet 139. Therefore, the oil passage 137 has a guide surface 145 that curves in the opposite direction to the rotation direction of the driven scroll 118 when the driving scroll 117 rotates in the forward direction from the through hole 134 and extends toward the inlet 139. Each guide surface 145 guides the oil flowing through the oil passage 137 toward the through hole 134.

<Oil groove 146>
As shown in FIG. 7, an oil groove 146 is formed on the inner circumferential surface of the through hole 134. The oil groove 146 is formed in a portion of the inner circumferential surface of the through hole 134 closer to the center L12 of the bush 133 than the center L13 of the through hole 134. Thus, the oil groove 146 is formed on the inner circumferential surface of the through hole 134, and in a portion that is out of phase with the portion on which the compressive load F1 transmitted from the driven scroll 118 acts between the inner circumferential surface of the through hole 134 and the outer circumferential surface of the eccentric shaft 132. Thus, the oil groove 146 is formed on the inner circumferential surface of the through hole 134, and in a portion excluding the portion on which the compressive load F1 transmitted from the driven scroll 118 acts between the inner circumferential surface of the through hole 134 and the outer circumferential surface of the eccentric shaft 132.

As shown in FIG. 6, the first end of the oil groove 146 is connected to the second end of the oil passage 137. The second end of the oil groove 146 opens to the end face of the bushing 133 on the driven spiral wall 118b side. The oil groove 146 connects the second end of the oil passage 137 to the space 147 between the end face of the bushing 133 on the driven spiral wall 118b side and the driven base plate 118a.

As shown in FIG. 8, the outer peripheral surface of the eccentric shaft 132 blocks the second end of the oil passage 137. The outer peripheral surface of the eccentric shaft 132 blocks the oil flowing through the oil passage 137 and guides it to the oil groove 146.

[Operation of the second embodiment]
Next, the operation of the second embodiment will be described.
Oil present around the bush 133 flows from the inlet 139 into the oil passage 137 and is supplied to the oil groove 146. The oil present around the bush 133 follows the rotation of the driven scroll 118 when the driving scroll 117 rotates in the forward direction and flows in the rotation direction of the driven scroll 118. At this time, the guide surface 145 curves from the through hole 134 in the opposite direction to the rotation direction of the driven scroll 118 when the driving scroll 117 rotates in the forward direction and extends toward the inlet 139. Therefore, the oil present around the bush 133 and flowing in the rotation direction of the driven scroll 118 is easily guided by the guide surface 145 toward the through hole 134 via the inlet 139. For this reason, the oil from the inlet 139 is easily supplied to the oil groove 146 via the oil passage 137. In addition, the oil flowing from the inlet 139 through the oil passage 137 is blocked by the outer circumferential surface of the eccentric shaft 132 and guided to the oil groove 146. This makes it easier for oil from the inlet 139 to be supplied to the oil groove 146 via the oil passage 137 .

The inlet 139 opens to a portion of the outer circumferential surface of the bush 133 that is located above the vertical direction Z1. This makes it easier for oil present around the bush 133 to fall under its own weight and flow into the inlet 139. This makes it easier for oil present around the bush 133 to flow from the inlet 139 into the oil passage 137 and be supplied to the oil groove 146.

Oil supplied to oil groove 146 passes through oil groove 146 and flows out into space 147 between the end face of bushing 133 on the driven spiral wall 118b side and driven base plate 118a. The oil that flows out into space 147 is then supplied to bearing 135. This ensures good lubrication of bearing 135.

[Effects of the second embodiment]
In the second embodiment, in addition to the effects (1-4) and (1-5) of the first embodiment, the following effects can be obtained.

(2-1) The bushing 133 has an oil passage 137 on the opposing surface 133a that faces the tip surface 105a of the support shaft 105. The oil passage 137 extends from the through hole 134 toward the outer peripheral surface of the bushing 133 and has an inlet 139 that opens into the outer peripheral surface of the bushing 133. An oil groove 146 is formed on the inner peripheral surface of the through hole 134, except for the portion where the compressive load F1 transmitted from the driven scroll 118 acts between the inner peripheral surface of the through hole 134 and the outer peripheral surface of the eccentric shaft 132. The oil groove 146 communicates with the oil passage 137 and opens into the end surface of the bushing 133 on the side of the driven scroll wall 118b. As a result, oil present around the bushing 133 flows from the inlet 139 into the oil passage 137 and is supplied to the oil groove 146. The oil supplied to the oil groove 146 passes through the oil groove 146 and flows out into the space 147 between the end face of the bush 133 on the driven spiral wall 118b side and the driven base plate 118a. The oil that flows out into the space 147 is then supplied to the bearing 135. This improves the lubrication of the bearing 135, improving the durability of the scroll compressor 100.

The oil groove 146 is formed on the inner circumferential surface of the through hole 134. Therefore, unlike the conventional technology, there is no need to form a through hole in the bush 133 other than the through hole 134 into which the eccentric shaft 132 is inserted in order to supply oil to the bearing 135. Therefore, there is no need to ensure the thickness of the bush 133. As a result, it is possible to avoid the bush 133 becoming larger. Therefore, it is possible to reduce the size of the scroll compressor 100. In addition, the oil groove 146 is formed on the inner circumferential surface of the through hole 134, and in a portion excluding the portion where the compression load F1 transmitted from the driven scroll 118 acts between the inner circumferential surface of the through hole 134 and the outer circumferential surface of the eccentric shaft 132. Therefore, even if the oil groove 146 is formed on the inner circumferential surface of the through hole 134, the rocking motion of the bush 133 about the eccentric shaft 132 is not hindered by the oil groove 146. As a result, it is possible to improve the durability while reducing the size of the scroll compressor 100.

(2-2) In this way, the scroll compressor 100 equipped with the driving scroll 117 and the driven scroll 118 can be made compact while improving durability.

(2-3) The inlet 139 opens to a portion of the outer circumferential surface of the bush 133 that is located above in the vertical direction Z1. This makes it easier for oil present around the bush 133 to fall under its own weight and flow into the inlet 139. This makes it easier for oil present around the bush 133 to flow from the inlet 139 into the oil passage 137 and be supplied to the oil groove 146. This further improves the lubrication of the bearing 135, thereby further improving the durability of the scroll compressor 100.

(2-4) The oil passage 137 has a guide surface 145 that curves in the opposite direction to the rotation direction of the driven scroll 118 when the driving scroll 117 rotates in the forward direction from the through hole 134 and extends toward the inlet 139. The guide surface 145 guides the oil flowing through the oil passage 137 toward the through hole 134. The oil present around the bush 133 follows the rotation of the driven scroll 118 when the driving scroll 117 rotates in the forward direction and flows in the rotation direction of the driven scroll 118. At this time, the guide surface 145 curves in the opposite direction to the rotation direction of the driven scroll 118 when the driving scroll 117 rotates in the forward direction from the through hole 134 and extends toward the inlet 139. Therefore, the oil present around the bush 133 and flowing in the rotation direction of the driven scroll 118 is easily guided by the guide surface 145 toward the through hole 134 via the inlet 139. This makes it easier for oil from the inlet 139 to be supplied to the oil groove 146 via the oil passage 137. As a result, oil is efficiently supplied to the bearing 135, which further improves the lubrication of the bearing 135. This further improves the durability of the scroll compressor 100.

[Example of change]
The above-described embodiments may be modified as follows: The above-described embodiments and the following modifications may be combined with each other to the extent that no technical contradiction occurs.

In the first embodiment, the compressive load F1 may act on the eccentric shaft 50 from a portion of the bushing cylindrical portion 52 that is closer to the center L2 of the bushing cylindrical portion 52 than the center L3 of the through hole 54. In this case, the oil groove 70 is formed in a portion of the inner circumferential surface of the through hole 54 that is closer to the center L3 of the through hole 54 than the center L2 of the bushing cylindrical portion 52. In short, it is sufficient that the oil groove 70 is formed on the inner circumferential surface of the through hole 54, except for the portion where the compressive load F1 acts.

In the second embodiment, the compressive load F1 may act on the eccentric shaft 132 from a portion of the bushing 133 closer to the center L12 of the bushing 133 than the center L13 of the through hole 134. In this case, the oil groove 146 is formed in a portion of the inner surface of the through hole 134 closer to the portion closer to the center L13 of the through hole 134 than the center L12 of the bushing 133. In short, it is sufficient that the oil groove 146 is formed on the inner surface of the through hole 134, except for the portion where the compressive load F1 acts.

In the second embodiment, the inlet 139 may open to a portion of the outer circumferential surface of the bush 133 that is located downward in the vertical direction Z1.
As shown in FIG. 9, in the first embodiment, the oil groove 70 may be formed on the outer peripheral surface of the eccentric shaft 50. In this case, the oil groove 70 is formed on the outer peripheral surface of the eccentric shaft 50, except for the portion on which the compression load F1 transmitted from the orbiting scroll 26 acts between the inner peripheral surface of the through hole 54 and the outer peripheral surface of the eccentric shaft 50. In the embodiment shown in FIG. 9, the oil groove 70 is not formed on the inner peripheral surface of the through hole 54. In addition, when the oil groove 70 is formed on the outer peripheral surface of the eccentric shaft 50, it is necessary to form the oil groove 70 at a position where the oil groove 70 and the oil passage 60 can always communicate with each other even if the bush 51 oscillates around the eccentric shaft 50. The oil groove 70 is relatively easy to form on the outer peripheral surface of the eccentric shaft 50. In this way, the configuration in which the oil groove 70 is formed on the outer peripheral surface of the eccentric shaft 50 can facilitate the design of the scroll compressor 10.

As shown in FIG. 10, in the second embodiment, the oil groove 146 may be formed on the outer peripheral surface of the eccentric shaft 132. In this case, the oil groove 146 is formed on the outer peripheral surface of the eccentric shaft 132, except for the portion on which the compressive load F1 transmitted from the driven scroll 118 acts between the inner peripheral surface of the through hole 134 and the outer peripheral surface of the eccentric shaft 132. In the embodiment shown in FIG. 10, the oil groove 146 is not formed on the inner peripheral surface of the through hole 134. In addition, when the oil groove 146 is formed on the outer peripheral surface of the eccentric shaft 132, it is necessary to form the oil groove 146 at a position where the oil groove 146 and the oil passage 137 can always communicate with each other even if the bush 133 oscillates around the eccentric shaft 132. It is relatively easy to form the oil groove 146 on the outer peripheral surface of the eccentric shaft 132. In this way, the configuration in which the oil groove 146 is formed on the outer peripheral surface of the eccentric shaft 132 can facilitate the design of the scroll compressor 100.

In the first embodiment, the oil groove 70 may be formed on both the inner circumferential surface of the through hole 54 and the outer circumferential surface of the eccentric shaft 50. In short, it is sufficient that the oil groove 70 is formed on at least one of the inner circumferential surface of the through hole 54 and the outer circumferential surface of the eccentric shaft 50, excluding the portion where the compressive load F1 transmitted from the orbiting scroll 26 acts between the inner circumferential surface of the through hole 54 and the outer circumferential surface of the eccentric shaft 50.

In the second embodiment, the oil groove 146 may be formed on both the inner circumferential surface of the through hole 134 and the outer circumferential surface of the eccentric shaft 132. In short, it is sufficient that the oil groove 146 is formed on at least one of the inner circumferential surface of the through hole 134 and the outer circumferential surface of the eccentric shaft 132, excluding the portion where the compressive load F1 transmitted from the driven scroll 118 acts between the inner circumferential surface of the through hole 134 and the outer circumferential surface of the eccentric shaft 132.

In the first embodiment, the first side 64 and the second side 65 of the passage forming recess 62 may extend straight from the outer peripheral surface of the eccentric shaft 50 toward the outer peripheral surface of the bush flange portion 53. In other words, the oil passage 60 does not need to have a guide surface 66.

In the second embodiment, the first side 143 and the second side 144 of the passage forming recess 141 may extend straight from the outer peripheral surface of the eccentric shaft 132 toward the outer peripheral surface of the bush 133. In other words, the oil passage 137 does not need to have a guide surface 145.

In the first embodiment, the second end of the oil passage 60 may open to the outer peripheral surface of the bush 51. In other words, the outer peripheral surface of the eccentric shaft 50 does not have to close the second end of the oil passage 60.

In the second embodiment, the second end of the oil passage 137 may open to the outer peripheral surface of the bush 133. In other words, the outer peripheral surface of the eccentric shaft 132 does not have to close the second end of the oil passage 137.

In the first embodiment, the eccentric shaft 50 is not integrally formed with the rotating shaft 15, and may be separate from the rotating shaft 15. In this case, the eccentric shaft 50 is attached to the tip surface 15e of the rotating shaft 15.

In the second embodiment, the eccentric shaft 132 may be formed integrally with the support shaft 105 .
In the first embodiment, the balance weight 55 may be separate from the bush 51 .

In each of the above embodiments, the

scroll compressor

10, 100 does not have to be a type that is driven by the

motor

22, 110, but may be a type that is driven by, for example, a vehicle engine.

In each of the above embodiments, the

scroll compressor

10, 100 is used in a vehicle air conditioner, but this is not limited to this. In short, the

scroll compressor

10, 100 may be used in any manner that compresses a refrigerant, and the use of the

scroll compressor

10, 100 may be changed as appropriate.

In each of the above-described embodiments, the object to be compressed by the

scroll compressors

10 and 100 is not limited to a refrigerant, but may be a fluid such as air.
Each of the above embodiments includes the configurations described in the following supplementary notes.

<Appendix 1>
Housing and
a support shaft supported relative to the housing;
a first scroll having a first base plate and a first scroll wall standing upright from the first base plate;
a second scroll including a second substrate facing the first substrate, and a second spiral wall rising from the second substrate toward the first substrate and meshing with the first spiral wall;
an eccentric shaft protruding from a tip end surface of the support shaft and extending parallel to the support shaft at a position eccentric with respect to an axis of the support shaft;
a bushing having a through hole into which the eccentric shaft is inserted and capable of swinging around the eccentric shaft;
a cylindrical holding portion provided on an end surface of the second substrate opposite to the first substrate, the bushing being disposed inside the cylindrical holding portion;
a bearing disposed between an inner circumferential surface of the retaining portion and an outer circumferential surface of the bush,
The bush is held by the holding portion via the bearing.
the bush has an oil passage on a surface facing the tip end surface of the support shaft,
the oil passage extends from the through hole toward an outer circumferential surface of the bush and has an inlet opening in the outer circumferential surface of the bush,
an oil groove communicating with the oil passage and opening into an end face of the bushing on the second scroll wall side is formed in at least one of an inner circumferential surface of the through hole and an outer circumferential surface of the eccentric shaft, excluding a portion where a compressive load transmitted from the second scroll acts between the inner circumferential surface of the through hole and the outer circumferential surface of the eccentric shaft.

<Appendix 2>
the support shaft is a rotation shaft rotatably supported with respect to the housing,
the first scroll is a fixed scroll having a fixed base plate as the first base plate and a fixed spiral wall as the first spiral wall standing up from the fixed base plate,
The second scroll is an orbiting scroll that has a rotating base plate as the second base plate facing the fixed base plate, and a orbiting spiral wall as the second spiral wall that stands from the orbiting base plate toward the fixed base plate and meshes with the fixed spiral wall, and that revolves by rotation of the rotation shaft.

<Appendix 3>
the oil passage has a guide surface that curves in a rotation direction of the bush when the rotation shaft rotates in a forward direction and extends from the through hole toward the inlet,
The scroll compressor according to <Appendix 2>, wherein the guide surface guides the oil flowing through the oil passage toward the through hole.

<Appendix 4>
the first scroll is a drive scroll having a drive substrate as the first substrate and a drive spiral wall as the first spiral wall standing from the drive substrate and rotating around an axis of the support shaft,
The second scroll is a driven scroll having a driven substrate as the second substrate facing the drive substrate, and a driven spiral wall as the second spiral wall rising from the driven substrate toward the drive substrate and meshing with the drive spiral wall, and rotating following the rotation of the drive scroll.

<Appendix 5>
The scroll compressor according to <Appendix 4>, wherein the inlet is open to a portion of the outer circumferential surface of the bush that is located vertically upward.

<Appendix 6>
The oil passage has a guide surface that curves in a direction opposite to a rotation direction of the driven scroll when the driving scroll rotates in a forward direction from the through hole toward the inlet,
The scroll compressor according to <Appendix 4> or <Appendix 5>, wherein the guide surface guides the oil flowing through the oil passage toward the through hole.

<Appendix 7>
The scroll compressor according to any one of <Appendix 1> to <Appendix 6>, wherein an outer peripheral surface of the eccentric shaft blocks oil flowing through the oil passage and guides it to the oil groove.

<Appendix 8>
The scroll compressor according to any one of <Appendix 1> to <Appendix 7>, wherein the oil groove is formed on an inner circumferential surface of the through hole.

<Appendix 9>
The scroll compressor according to any one of <Appendix 1> to <Appendix 7>, wherein the oil groove is formed on an outer circumferential surface of the eccentric shaft.

10,100...Scroll type compressor, 11,101...Housing, 15...Rotating shaft (support shaft), 15e...Tip surface, 25...Fixed scroll (first scroll), 25a...Fixed base plate (first base plate), 25b...Fixed spiral wall (first spiral wall), 26...Orbiting scroll (second scroll), 26a...Orbiting base plate (second base plate), 26b...Orbiting spiral wall (second spiral wall), 26e...End surface, 28...Boss portion (retaining portion), 50,132...Eccentric shaft, 51,133...Bush, 51a,133a... Opposing surface, 54, 134...through hole, 56, 135...bearing, 60, 137...oil passage, 61, 139...inlet, 66, 145...guide surface, 70, 146...oil groove, 105...support shaft, 105a...tip surface, 117...driving scroll (first scroll), 117a...driving substrate (first substrate), 117b...driving spiral wall (first spiral wall), 118...driven scroll (second scroll), 118a...driven substrate (second substrate), 118b...driven spiral wall (second spiral wall), 130...retaining portion.

Claims

Housing and
a support shaft supported relative to the housing;
a first scroll having a first base plate and a first scroll wall standing upright from the first base plate;
a second scroll including a second substrate facing the first substrate, and a second spiral wall rising from the second substrate toward the first substrate and meshing with the first spiral wall;
an eccentric shaft protruding from a tip end surface of the support shaft and extending parallel to the support shaft at a position eccentric with respect to an axis of the support shaft;
a bushing having a through hole into which the eccentric shaft is inserted and capable of swinging around the eccentric shaft;
a cylindrical holding portion provided on an end surface of the second substrate opposite to the first substrate, the bushing being disposed inside the cylindrical holding portion;
a bearing disposed between an inner circumferential surface of the retaining portion and an outer circumferential surface of the bush,
The bush is held by the holding portion via the bearing.
The bush has an oil passage on a surface facing the tip end surface of the support shaft,
the oil passage extends from the through hole toward an outer circumferential surface of the bush and has an inlet opening in the outer circumferential surface of the bush,
an oil groove communicating with the oil passage and opening into an end face of the bushing on the second scroll wall side is formed in at least one of an inner circumferential surface of the through hole and an outer circumferential surface of the eccentric shaft, excluding a portion where a compressive load transmitted from the second scroll acts between the inner circumferential surface of the through hole and the outer circumferential surface of the eccentric shaft.
the support shaft is a rotation shaft rotatably supported with respect to the housing,
the first scroll is a fixed scroll having a fixed base plate as the first base plate and a fixed spiral wall as the first spiral wall standing up from the fixed base plate,
2. The scroll compressor according to claim 1, wherein the second scroll is an orbiting scroll that has a rotating base plate as the second base plate facing the fixed base plate, and a orbiting spiral wall as the second spiral wall that stands from the orbiting base plate toward the fixed base plate and meshes with the fixed spiral wall, and that revolves by rotation of the rotating shaft.
the oil passage has a guide surface that curves in a rotation direction of the bush when the rotation shaft rotates in a forward direction from the through hole toward the inlet,
The scroll compressor according to claim 2 , wherein the guide surface guides the oil flowing through the oil passage toward the through hole.
the first scroll is a drive scroll having a drive substrate as the first substrate and a drive spiral wall as the first spiral wall standing from the drive substrate and rotating around an axis of the support shaft,
2. The scroll-type compressor according to claim 1, wherein the second scroll is a driven scroll that rotates following the rotation of the driving scroll, the driven scroll having a driven substrate as the second substrate facing the driving substrate, and a driven spiral wall as the second spiral wall that stands from the driven substrate toward the driving substrate and meshes with the driving spiral wall.
The scroll compressor according to claim 4, characterized in that the inlet opens to a portion of the outer circumferential surface of the bush that is located vertically above the bush.
The oil passage has a guide surface that curves in a direction opposite to a rotation direction of the driven scroll when the driving scroll rotates in a forward direction from the through hole toward the inlet,
6. The scroll compressor according to claim 4, wherein the guide surface guides the oil flowing through the oil passage toward the through hole.
The scroll compressor according to any one of claims 1 to 6, characterized in that the outer peripheral surface of the eccentric shaft blocks the oil flowing through the oil passage and guides it to the oil groove.
The scroll compressor according to claim 1, characterized in that the oil groove is formed on the inner circumferential surface of the through hole.
The scroll compressor according to claim 1, characterized in that the oil groove is formed on the outer peripheral surface of the eccentric shaft.