JP2021188553A - Scroll type compressor - Google Patents

Abstract

To improve the lubricity of a thrust bearing part.SOLUTION: A first opposite face 62 has a slide surface 65 on which a plurality of pressure receiving parts 75 slide when a moving scroll 32 revolves, and a non-slide surface 66 on which the plurality of pressure receiving parts 75 do not slide when the moving scroll 32 revolves. The surface roughness of the non-slide surface 66 is greater than the surface roughness of the slide surface 65. Thus, on the first opposite face 62, the amount of oil held on the non-slide surface 66 becomes greater, for example, compared to the case that the surface roughness of the non-slide surface 66 is not greater than the surface roughness of the slide surface 65. As a result, the oil held on the non-slide surface 66 is easily supplied in between each pressure receiving part 75 and the slide surface 65 along with the revolution of the moving scroll 32.SELECTED DRAWING: Figure 4

Description

The present invention relates to a scroll type compressor.

The scroll type compressor includes a fixed scroll and a movable scroll arranged opposite to the fixed scroll. The movable scroll compresses the fluid by revolving with respect to the fixed scroll while the rotation is blocked by the rotation blocking mechanism. The movable scroll receives a thrust load due to the pressure difference between the pressure of the fluid compressed by the revolving motion of the movable scroll and the pressure acting on the back surface of the movable scroll opposite to the fixed scroll. In particular, in a scroll type compressor that uses carbon dioxide as the refrigerant to be compressed, the pressure of the compressed refrigerant is high, so that the thrust load received by the movable scroll becomes large.

Therefore, as disclosed in Patent Document 1, for example, a scroll type compressor provided with a thrust bearing portion that receives a thrust load from a movable scroll has been conventionally known. In such a thrust bearing portion, a first facing surface made of a coating layer and a plurality of pressure receiving portions facing the first facing surface and projecting toward the first facing surface and sliding on the first facing surface are formed. It also has a second facing surface.

In such a configuration, the oil supplied between the first facing surface and the second facing surface reaches each pressure receiving portion and the first facing surface from the periphery of each pressure receiving portion due to the wedge effect of the peripheral portion of each pressure receiving portion. It becomes easy to be drawn in between. For this reason, oil is easily supplied between each pressure receiving portion and the first facing surface, so that an oil film is easily formed between each pressure receiving portion and the first facing surface, and each pressure receiving portion and the first facing surface are easily formed. Friction between and is less likely to occur. As a result, the lubricity of the thrust bearing portion becomes good.

Further, in particular, in Patent Document 1, a diamond-like carbon layer is adopted as a coating layer on the surface of the first facing surface. Therefore, for example, the scroll type compressor is operated in a situation where it is difficult to supply oil between the first facing surface and the second facing surface, and an oil film is formed between each pressure receiving portion and the first facing surface. Even if it is difficult to form, friction between each pressure receiving portion and the first facing surface is unlikely to occur.

Japanese Unexamined Patent Publication No. 2010-174902

However, for example, even when the scroll type compressor is operated in a situation where it is difficult to supply oil between the first facing surface and the second facing surface, each pressure receiving portion and the first facing surface can be used. There is a desire to improve the lubricity of the thrust bearing portion by forming an oil film between them.

The present invention has been made to solve the above problems, and an object of the present invention is to provide a scroll type compressor capable of improving the lubricity of a thrust bearing portion.

The scroll type compressor that solves the above-mentioned problems is a movable type that is arranged to face the fixed scroll and the fixed scroll, and compresses the fluid by revolving with respect to the fixed scroll in a state where the rotation is prevented by the rotation prevention mechanism. The thrust includes a scroll, an opposing member arranged on the side opposite to the fixed scroll with respect to the movable scroll, and a thrust bearing portion that receives a thrust load from the movable scroll on the facing member side. The bearing portion is formed with a first facing surface made of a coating layer and a plurality of pressure receiving portions facing the first facing surface and projecting toward the first facing surface and sliding on the first facing surface. It has a second facing surface, and a plurality of pins constituting the rotation prevention mechanism are projected from the first facing surface, and the plurality of pins are inserted into the second facing surface. An insertion portion is formed, one of the first facing surface and the second facing surface revolves together with the movable scroll, and the other of the first facing surface and the second facing surface is fixed to the facing member. The first facing surface is a sliding surface on which the plurality of pressure receiving portions slide when the movable scroll revolves, and a non-sliding surface on which the plurality of pressure receiving portions do not slide when the movable scroll revolves. The non-sliding surface is provided at a position where at least a part thereof overlaps with each insertion portion in the axial direction, and the surface roughness of the non-sliding surface is the surface roughness of the sliding surface. Greater than surface roughness.

According to this, on the first facing surface, for example, the amount of oil held on the non-sliding surface is increased as compared with the case where the surface roughness of the non-sliding surface is equal to or less than the surface roughness of the sliding surface. You can do a lot. Therefore, the oil held on the non-sliding surface is easily supplied between each pressure receiving portion and the sliding surface as the movable scroll revolves, and an oil film is formed between each pressure receiving portion and the sliding surface. Is likely to be formed. As a result, for example, even when the scroll type compressor is operated in a situation where it is difficult to supply oil between the first facing surface and the second facing surface, each pressure receiving portion and the first facing surface are operated. An oil film can be easily formed between the and the thrust bearing portion, and the lubricity of the thrust bearing portion can be improved.

In the scroll type compressor, it is preferable that the first facing surface revolves together with the movable scroll, and the second facing surface is fixed to the facing member.
According to this, the centrifugal force accompanying the revolution movement of the movable scroll acts on the oil held on the non-sliding surface, and the oil held on the non-sliding surface is released from the non-sliding surface by the centrifugal force. It becomes easy to be blown away. As a result, the oil held on the non-sliding surface is easily supplied between each pressure receiving portion and the sliding surface, so that an oil film is easily formed between each pressure receiving portion and the sliding surface. Therefore, the lubricity of the thrust bearing portion can be further improved.

In the scroll type compressor, at least a part of the non-sliding surface may be provided at a position on the outer peripheral side in the radial direction with respect to the sliding surface.
According to this, even if the centrifugal force due to the revolution movement of the movable scroll acts on the oil between each pressure receiving portion and the sliding surface, the oil is blown off to the outer peripheral side in the radial direction with respect to the sliding surface. The oil can be held by the non-sliding surface provided at a position on the outer peripheral side in the radial direction with respect to the sliding surface. Therefore, the oil held on the non-sliding surface is easily supplied between each pressure receiving portion and the sliding surface as the movable scroll revolves, and an oil film is formed between each pressure receiving portion and the sliding surface. Is likely to be formed. As a result, the lubricity of the thrust bearing portion can be further improved.

In the scroll type compressor, a part of the non-sliding surface does not overlap with each of the insertion portions when the movable scroll revolves, and the position is on the outer peripheral side in the radial direction with respect to the sliding surface. It is good that it is provided in.

According to this, for example, as compared with the case where the non-sliding surface is formed only in the portion of the first facing surface that overlaps with each insertion portion in the axial direction when the movable scroll revolves. 1 The area of the non-sliding surface on the facing surface can be increased. Therefore, since the amount of oil held on the non-sliding surface increases, the oil held on the non-sliding surface is more likely to be supplied between each pressure receiving portion and the sliding surface, and each pressure receiving portion. An oil film is more likely to be formed between the surface and the sliding surface. As a result, the lubricity of the thrust bearing portion can be further improved.

In the scroll type compressor, the surface roughness of the non-sliding surface is preferably 10 μm to 20 μm, and the surface roughness of the sliding surface is preferably 5 μm or less.
A non-sliding surface having a surface roughness of 10 μm to 20 μm is suitable as a non-sliding surface for holding oil. Further, the sliding surface having a surface roughness of 5 μm or less is suitable as a sliding surface for forming an oil film between each pressure receiving portion and the sliding surface.

According to the present invention, the lubricity of the thrust bearing portion can be improved.

A side sectional view showing a scroll type compressor in an embodiment. The cross-sectional view which shows the 1st facing surface of the 1st thrust bearing plate. The cross-sectional view which shows the 2nd facing surface of the 2nd thrust bearing plate. The cross-sectional view which shows the thrust bearing part enlarged. FIG. 3 is an enlarged cross-sectional view showing the first facing surface. FIG. 3 is an enlarged cross-sectional view showing a state before the pressure receiving portion slides on the first facing surface. FIG. 3 is an enlarged cross-sectional view showing a state in which the pressure receiving portion is slid on the first facing surface. FIG. 3 is an enlarged cross-sectional view showing a state after the pressure receiving portion has slid on the first facing surface.

Hereinafter, an embodiment in which the scroll type compressor is embodied will be described with reference to FIGS. 1 to 8. The scroll type compressor of this embodiment is used, for example, in a vehicle air conditioner.
As shown in FIG. 1, the scroll type compressor 10 includes a tubular housing 11, a rotating shaft 12 housed in the housing 11, a compression mechanism 13 driven by the rotation of the rotating shaft 12, and a rotating shaft 12. It is provided with an electric motor 14 for rotating.

The housing 11 includes a motor housing 15, a discharge housing 16, and an inverter cover 17. The motor housing 15, the discharge housing 16, and the inverter cover 17 are each made of a metal material, for example, aluminum.

The motor housing 15 has a bottomed tubular shape having a bottom wall 15a and a peripheral wall 15b extending in a cylindrical shape from the outer peripheral portion of the bottom wall 15a. The direction in which the axis of the peripheral wall 15b extends coincides with the axial direction in which the axis L1 of the rotating shaft 12 extends. A female screw hole 15c is formed on the open end surface of the peripheral wall 15b. A suction port 15h is formed on the peripheral wall 15b. The suction port 15h is formed in a portion of the peripheral wall 15b located on the bottom wall 15a side. The suction port 15h communicates with the inside and outside of the motor housing 15.

The inverter cover 17 is attached to the bottom wall 15a of the motor housing 15. An inverter device 18 for driving the electric motor 14 is housed in a space partitioned by the inverter cover 17 and the bottom wall 15a of the motor housing 15. In FIG. 1, the inverter device 18 is shown by a broken line.

A cylindrical boss portion 15f is projected on the inner surface of the bottom wall 15a. One end of the rotating shaft 12 is inserted into the boss portion 15f. A cylindrical slide bearing 19 is provided between the inner peripheral surface of the boss portion 15f and the outer peripheral surface of one end of the rotating shaft 12. One end of the rotary shaft 12 is rotatably supported by the boss portion 15f of the motor housing 15 via the slide bearing 19.

A bottomed cylindrical shaft support member 20 is provided in the motor housing 15. The shaft support member 20 is fixed near the opening of the motor housing 15. An insertion hole 21 through which the rotating shaft 12 is inserted is formed in the central portion of the shaft support member 20. The axis of the insertion hole 21 coincides with the axis of the peripheral wall 15b of the motor housing 15.

The motor housing 15 and the shaft support member 20 partition the motor chamber 22 formed in the housing 11. A refrigerant as a fluid is sucked into the motor chamber 22 from an external refrigerant circuit (not shown) via the suction port 15h. Therefore, the motor chamber 22 is a suction chamber in which the refrigerant is sucked from the suction port 15h. In the present embodiment, carbon dioxide is adopted as the refrigerant sucked into the motor chamber 22 from the external refrigerant circuit via the suction port 15h.

The insertion hole 21 has a large diameter hole 21a and a small diameter hole 21b having a smaller diameter than the large diameter hole 21a. The large-diameter hole 21a is located on the side opposite to the motor chamber 22 with respect to the small-diameter hole 21b. One end of the large-diameter hole 21a is open to the end surface of the shaft support member 20 opposite to the motor chamber 22. The other end of the large diameter hole 21a communicates with one end of the small diameter hole 21b. The other end of the small diameter hole 21b is open to the end of the shaft support member 20 on the motor chamber 22 side.

The end surface 12e on the other end side of the rotating shaft 12 is located inside the insertion hole 21 of the shaft support member 20. A cylindrical slide bearing 23 is provided between the outer peripheral surface of the other end of the rotating shaft 12 and the inner peripheral surface of the small diameter hole 21b of the insertion hole 21. The rotary shaft 12 is rotatably supported by the shaft support member 20 via the slide bearing 23.

A first seal member 24 is provided between a portion of the inner peripheral surface of the small diameter hole 21b on the side of the large diameter hole 21a with respect to the slide bearing 23 and the outer peripheral surface of the rotating shaft 12. The first sealing member 24 seals between the inner peripheral surface of the small diameter hole 21b and the outer peripheral surface of the rotary shaft 12 at a portion on the inner peripheral surface of the small diameter hole 21b on the side of the large diameter hole 21a with respect to the slide bearing 23. There is. Further, a second seal member 25 is provided between a portion of the inner peripheral surface of the small diameter hole 21b opposite to the large diameter hole 21a side of the slide bearing 23 and the outer peripheral surface of the rotating shaft 12. The second seal member 25 is a portion of the inner peripheral surface of the small diameter hole 21b opposite to the large diameter hole 21a of the slide bearing 23, and is between the inner peripheral surface of the small diameter hole 21b and the outer peripheral surface of the rotary shaft 12. It is sealed.

An electric motor 14 is housed in the motor chamber 22. The electric motor 14 has a cylindrical stator 26 and a rotor 27 arranged inside the stator 26. The rotor 27 rotates integrally with the rotating shaft 12. The stator 26 surrounds the rotor 27. The rotor 27 has a rotor core 27a anchored to the rotating shaft 12 and a plurality of permanent magnets (not shown) provided on the rotor core 27a. The stator 26 has a cylindrical stator core 26a fixed to the inner peripheral surface of the peripheral wall 15b of the motor housing 15, and a coil 26b wound around the stator core 26a. Then, the electric power controlled by the inverter device 18 is supplied to the coil 26b to rotate the rotor 27, and the rotating shaft 12 rotates integrally with the rotor 27.

The discharge housing 16 has a block shape. The discharge housing 16 is attached to the open end surface of the peripheral wall 15b of the motor housing 15 via a plate-shaped gasket 28. Specifically, the discharge housing 16 is attached to the motor housing 15 by screwing a bolt 29 penetrating the discharge housing 16 and the gasket 28 into the female screw hole 15c. The gasket 28 seals between the discharge housing 16 and the motor housing 15.

The compression mechanism 13 has a fixed scroll 31 and a movable scroll 32 arranged to face the fixed scroll 31. The fixed scroll 31 and the movable scroll 32 are arranged inside the peripheral wall 15b of the motor housing 15 on the side opposite to the motor chamber 22 with respect to the shaft support member 20. Therefore, the peripheral wall 15b of the motor housing 15 covers the compression mechanism 13 on the radial outer side of the rotating shaft 12. That is, the peripheral wall 15b of the motor housing 15 surrounds the compression mechanism 13.

The fixed scroll 31 is located closer to the discharge housing 16 than the movable scroll 32 in the axial direction of the rotating shaft 12. Therefore, the shaft support member 20 is an opposing member arranged on the side opposite to the fixed scroll 31 with respect to the movable scroll 32. In the present embodiment, the compression mechanism 13, the electric motor 14, and the inverter device 18 are arranged side by side in the axial direction of the rotating shaft 12 in this order.

The fixed scroll 31 has a disk-shaped fixed substrate 31a and a fixed spiral wall 31b erected from the fixed substrate 31a toward the side opposite to the discharge housing 16. Further, the fixed scroll 31 has a fixed outer peripheral wall 31c extending in a cylindrical shape from the outer peripheral portion of the fixed substrate 31a. The fixed outer peripheral wall 31c surrounds the fixed spiral wall 31b. The open end surface of the fixed outer peripheral wall 31c is located on the side opposite to the fixed substrate 31a with respect to the tip surface of the fixed spiral wall 31b.

The movable scroll 32 has a disk-shaped movable substrate 32a facing the fixed substrate 31a, and a movable spiral wall 32b erected from the movable substrate 32a toward the fixed substrate 31a. The fixed spiral wall 31b and the movable spiral wall 32b are meshed with each other. The movable spiral wall 32b is located inside the fixed outer peripheral wall 31c. The tip surface of the fixed spiral wall 31b is in contact with the movable substrate 32a, and the tip surface of the movable spiral wall 32b is in contact with the fixed substrate 31a. A plurality of compression chambers 33 in which the refrigerant is compressed are partitioned by the fixed substrate 31a, the fixed spiral wall 31b, the fixed outer peripheral wall 31c, the movable substrate 32a, and the movable spiral wall 32b.

A circular hole-shaped discharge port 31h is formed in the central portion of the fixed substrate 31a. The discharge port 31h penetrates the fixed substrate 31a in the thickness direction. A discharge valve mechanism 34 that opens and closes the discharge port 31h is attached to the end surface of the fixed substrate 31a on the side opposite to the movable scroll 32.

A cylindrical boss portion 32f is projected from the back surface 32e, which is the end surface of the movable substrate 32a on the opposite side to the fixed substrate 31a. The axial direction of the boss portion 32f coincides with the axial direction of the rotating shaft 12. The boss portion 32f is located inside the large diameter hole 21a of the shaft support member 20.

The fixed scroll 31 is positioned with respect to the motor housing 15 in a state where rotation about the axis L1 of the rotating shaft 12 inside the peripheral wall 15b of the motor housing 15 is restricted. The fixed scroll 31 closes the opening of the motor housing 15. The open end surface of the fixed outer peripheral wall 31c faces the end surface of the shaft support member 20 opposite to the motor chamber 22 via the plate 35.

An eccentric shaft 36 that protrudes toward the movable scroll 32 from a position eccentric with respect to the axis L1 of the rotating shaft 12 is integrally formed on the end surface 12e on the other end side of the rotating shaft 12. The axial direction of the eccentric shaft 36 coincides with the axial direction of the rotating shaft 12. The eccentric shaft 36 is located inside the large diameter hole 21a of the shaft support member 20. The eccentric shaft 36 is inserted in the boss portion 32f.

A bush 38 with a balance weight 37 integrated is fitted on the outer peripheral surface of the eccentric shaft 36. The balance weight 37 is integrally formed with the bush 38. The balance weight 37 is housed in the large diameter hole 21a of the shaft support member 20. The movable scroll 32 is supported by the eccentric shaft 36 so as to be rotatable relative to the eccentric shaft 36 via the bush 38 and the slide bearing 39.

A through hole 40 is formed in the outer peripheral portion of the shaft support member 20. The plate 35 is formed with a communication hole 41 that communicates with the through hole 40. An introduction recess 42 communicating with the communication hole 41 is formed on the outer peripheral surface of the fixed outer peripheral wall 31c of the fixed scroll 31. Further, the fixed outer peripheral wall 31c is formed with a through hole 43 for communicating the introduction recess 42 and the outermost peripheral portion of the compression chamber 33.

A chamber forming recess 44 is formed on the end surface of the discharge housing 16 on the motor housing 15 side. The discharge chamber 45 is partitioned by the chamber forming recess 44 and the fixed substrate 31a of the fixed scroll 31. Further, a discharge port 46 is formed in the discharge housing 16. An external refrigerant circuit is connected to the discharge port 46. Further, an oil separation chamber 47 is formed in the discharge housing 16. The oil separation chamber 47 communicates with the discharge port 46. The oil separation chamber 47 is provided with an oil separation cylinder 48. Further, the discharge housing 16 is formed with a discharge hole 49 that communicates the discharge chamber 45 and the oil separation chamber 47. Further, an oil storage chamber 50 is formed in the discharge housing 16. The oil storage chamber 50 communicates with the oil separation chamber 47.

The refrigerant compressed in the compression chamber 33 is discharged from the discharge port 31h to the discharge chamber 45 via the discharge valve mechanism 34. The refrigerant discharged to the discharge chamber 45 flows out to the oil separation chamber 47 through the discharge hole 49, and the oil contained in the refrigerant is separated from the refrigerant by the oil separation cylinder 48 in the oil separation chamber 47. Then, the refrigerant from which the oil has been separated flows into the oil separation cylinder 48 and is discharged to the external refrigerant circuit via the discharge port 46. The refrigerant discharged to the external refrigerant circuit returns to the motor chamber 22 via the suction port 15h. On the other hand, the oil separated from the refrigerant by the oil separation cylinder 48 flows from the oil separation chamber 47 toward the oil storage chamber 50 and is stored in the oil storage chamber 50.

The scroll type compressor 10 includes an oil introduction path 51. The oil introduction path 51 penetrates the discharge housing 16, the gasket 28, the fixed scroll 31, the plate 35, and the shaft support member 20. One end of the oil introduction path 51 communicates with the oil storage chamber 50. The other end of the oil introduction path 51 is open between the slide bearing 23 and the first seal member 24 in the small diameter hole 21b.

An axis 52 and a path 53 are formed on the rotating shaft 12. The axis 52 extends in the axial direction of the rotating shaft 12. One end of the shaft path 52 opens at one end surface of the rotating shaft 12 and communicates with the inside of the boss portion 15f. The other end of the shaft path 52 is closed inside the rotary shaft 12 near the other end. The route 53 extends in the radial direction of the rotating shaft 12. One end of the path 53 is open between the slide bearing 23 and the second seal member 25 in the small diameter hole 21b. The other end of the path 53 communicates with the other end of the axis 52.

The oil stored in the oil storage chamber 50 flows into the small diameter hole 21b between the slide bearing 23 and the first seal member 24 through the oil introduction path 51, and flows into the inner peripheral surface of the slide bearing 23 and the rotary shaft 12. It is supplied between the outer peripheral surface and the outer peripheral surface. As a result, an oil film is formed between the inner peripheral surface of the slide bearing 23 and the outer peripheral surface of the rotary shaft 12, and the lubricity between the slide bearing 23 and the rotary shaft 12 is maintained. Further, the oil passes between the inner peripheral surface of the slide bearing 23 and the outer peripheral surface of the rotary shaft 12, flows in between the slide bearing 23 and the second seal member 25 in the small diameter hole 21b, and flows into the path 53. And, it passes through the axis 52 and flows into the boss portion 15f. The oil that has flowed into the boss portion 15f is supplied between the inner peripheral surface of the slide bearing 19 and the outer peripheral surface of the rotating shaft 12. As a result, an oil film is formed between the inner peripheral surface of the slide bearing 19 and the outer peripheral surface of the rotary shaft 12, and the lubricity between the slide bearing 19 and the rotary shaft 12 is maintained. Then, the oil passes between the inner peripheral surface of the slide bearing 19 and the outer peripheral surface of the rotating shaft 12, and is returned to the motor chamber 22.

A back pressure chamber 54 is formed in the housing 11. The back pressure chamber 54 is located between the shaft support member 20 and the movable scroll 32. The back pressure chamber 54 is formed in the housing 11 at a position opposite to the fixed substrate 31a with respect to the movable substrate 32a. The inside of the large-diameter hole 21a is a back pressure chamber 54. The shaft support member 20 separates the back pressure chamber 54 and the motor chamber 22.

The movable scroll 32 is formed with a back pressure introduction passage 55 that penetrates the movable substrate 32a and the movable swirl wall 32b. The back pressure introduction passage 55 introduces the refrigerant in the compression chamber 33 into the back pressure chamber 54. The back pressure chamber 54 has a higher pressure than the motor chamber 22 because the refrigerant in the compression chamber 33 is introduced through the back pressure introduction passage 55. The pressure in the back pressure chamber 54 acts on the back surface 32e of the movable substrate 32a. Then, as the pressure in the back pressure chamber 54 increases, the movable scroll 32 is urged toward the fixed scroll 31 so that the tip surface of the movable spiral wall 32b is pressed against the fixed substrate 31a.

The scroll type compressor 10 includes a thrust bearing portion 60 that receives a thrust load from the movable scroll 32 on the shaft support member 20 side. The thrust bearing portion 60 includes a disk-shaped first thrust bearing plate 61 and a disk-shaped second thrust bearing plate 71.

The first thrust bearing plate 61 is fixed to the back surface 32e of the movable substrate 32a of the movable scroll 32. The thickness direction of the first thrust bearing plate 61 coincides with the thickness direction of the movable substrate 32a. The second thrust bearing plate 71 is fixed to the end surface of the shaft support member 20 opposite to the motor chamber 22. The thickness direction of the second thrust bearing plate 71 coincides with the direction in which the axial center of the insertion hole 21 of the shaft support member 20 extends. The second thrust bearing plate 71 is made of, for example, steel.

The first thrust bearing plate 61 and the second thrust bearing plate 71 are arranged between the movable scroll 32 and the shaft support member 20. Therefore, the thrust bearing portion 60 is arranged between the movable scroll 32 and the shaft support member 20. The thrust bearing portion 60 exists in the refrigerant atmosphere in the back pressure chamber 54. The first thrust bearing plate 61 and the second thrust bearing plate 71 face each other in the axial direction of the rotating shaft 12. The thickness direction of the first thrust bearing plate 61 and the thickness direction of the second thrust bearing plate 71 coincide with each other. The end surface of the first thrust bearing plate 61 on the side opposite to the movable substrate 32a is the first facing surface 62 facing the second thrust bearing plate 71. The end surface of the second thrust bearing plate 71 opposite to the shaft support member 20 is a second facing surface 72 facing the first facing surface 62 of the first thrust bearing plate 61. Therefore, the thrust bearing portion 60 has a first facing surface 62 and a second facing surface 72.

As shown in FIGS. 1 and 2, the first thrust bearing plate 61 is formed with a first through hole 63. The first through hole 63 penetrates the first thrust bearing plate 61 in the thickness direction. The hole diameter of the first through hole 63 is larger than the outer diameter of the boss portion 32f. The boss portion 32f passes through the inside of the first through hole 63. A plurality of pins 64 project from the first facing surface 62. In the present embodiment, six pins 64 are projected from the first facing surface 62. Each pin 64 is cylindrical. The six pins 64 are arranged at equal intervals in the circumferential direction of the first thrust bearing plate 61.

As shown in FIGS. 1 and 3, a second through hole 73 is formed in the second thrust bearing plate 71. The second through hole 73 penetrates the second thrust bearing plate 71 in the thickness direction. The hole diameter of the second through hole 73 is the same as the hole diameter of the large diameter hole 21a of the shaft support member 20. The axis of the second through hole 73 and the axis of the large diameter hole 21a coincide with each other. The second facing surface 72 is formed with an insertion hole 74 as an insertion portion into which a plurality of pins 64 are inserted. Therefore, in the present embodiment, six insertion holes 74 are formed in the second facing surface 72. Each insertion hole 74 penetrates the second thrust bearing plate 71 in the thickness direction. Each insertion hole 74 has a circular hole shape. The hole diameter of each insertion hole 74 is the same. The six insertion holes 74 are arranged at equal intervals in the circumferential direction of the second thrust bearing plate 71.

As shown in FIG. 1, an insertion recess 20a communicating with each insertion hole 74 is formed on the end surface of the shaft support member 20 on the side opposite to the motor chamber 22. Each insertion recess 20a has a circular hole shape having the same shape as each insertion hole 74. The inner peripheral surface of each insertion recess 20a and the inner peripheral surface of each insertion hole 74 overlap each other in the thickness direction of the second thrust bearing plate 71. Each pin 64 is loosely fitted to each insertion hole 74 and each insertion recess 20a.

The rotation of the rotating shaft 12 is transmitted to the movable scroll 32 via the eccentric shaft 36, the bush 38, and the slide bearing 39, and the movable scroll 32 rotates on its axis. When each pin 64 comes into contact with the inner peripheral surface of each insertion hole 74 and the inner peripheral surface of each insertion recess 20a, the rotation of the movable scroll 32 is prevented, and only the revolution movement of the movable scroll 32 is allowed. Scroll. As a result, the movable scroll 32 revolves while the movable spiral wall 32b is in contact with the fixed spiral wall 31b, and the volume of the compression chamber 33 is reduced. Therefore, each pin 64 and each insertion hole 74 constitutes a rotation prevention mechanism 80 that prevents the rotation of the movable scroll 32. The balance weight 37 cancels the centrifugal force acting on the movable scroll 32 when the movable scroll 32 revolves, and reduces the unbalanced amount of the movable scroll 32.

Then, the refrigerant sucked into the motor chamber 22 is sucked into the outermost peripheral portion of the compression chamber 33 through the through hole 40, the communication hole 41, the introduction recess 42, and the through hole 43. The refrigerant sucked into the outermost peripheral portion of the compression chamber 33 is compressed in the compression chamber 33 by the revolution motion of the movable scroll 32. Therefore, the movable scroll 32 compresses the refrigerant by revolving with respect to the fixed scroll 31 in a state where the rotation is prevented by the rotation prevention mechanism 80.

The first thrust bearing plate 61 revolves together with the movable scroll 32. Therefore, the first facing surface 62 revolves together with the movable scroll 32. On the other hand, the second thrust bearing plate 71 is fixed to the shaft support member 20. Therefore, the second facing surface 72 is fixed to the shaft support member 20.

As shown in FIGS. 3 and 4, a plurality of pressure receiving portions 75 projecting toward the first facing surface 62 are formed on the second facing surface 72 of the second thrust bearing plate 71. Therefore, the thrust bearing portion 60 has a plurality of pressure receiving portions 75. As shown in FIG. 3, a plurality of pressure receiving portions 75 are arranged side by side in the circumferential direction of the second thrust bearing plate 71 and are arranged in a staggered manner.

As shown in FIG. 4, each pressure receiving portion 75 is a columnar shape protruding from the second facing surface 72. The direction in which the axis L10 of each pressure receiving portion 75 extends is a direction orthogonal to the second facing surface 72. The outer peripheral surface 75a of each pressure receiving portion 75 is continuous with the second facing surface 72. The tip surface of each pressure receiving portion 75 is a flat surface 75f. The entire peripheral edge portion, which is a corner portion between the outer peripheral surface 75a and the flat surface 75f of each pressure receiving portion 75, is a chamfered portion 75e chamfered in an arc shape. Therefore, the chamfered portion 75e of each pressure receiving portion 75 is annular. The flat surface 75f of each pressure receiving portion 75 has a circular shape when viewed in a plan view. The flat surface 75f of each pressure receiving portion 75 slides on the first facing surface 62 of the first thrust bearing plate 61.

As shown in FIG. 2, the first facing surface 62 of the first thrust bearing plate 61 has a sliding surface 65 on which a plurality of pressure receiving portions 75 slide when the movable scroll 32 revolves, and the movable scroll 32 revolves. It has a non-sliding surface 66 on which the plurality of pressure receiving portions 75 do not slide when exercising. In FIG. 2, the white portion of the first facing surface 62 that is not dot-hatched is the sliding surface 65. Further, in FIG. 2, the portion of the first facing surface 62 where the dot hatching is applied is the non-sliding surface 66.

In FIG. 5, the locus of the position of the first thrust bearing plate 61 with respect to the first facing surface 62 on the axis L10 of each pressure receiving portion 75 when the movable scroll 32 revolves is shown by a virtual circle C1. Therefore, each virtual circle C1 shows the locus of the position of the first thrust bearing plate 61 in each pressure receiving portion 75 with respect to the first facing surface 62 when the movable scroll 32 revolves. The white portion of the first facing surface 62 shown in FIG. 5 without dot hatching is a region through which each pressure receiving portion 75 passes when the movable scroll 32 revolves. Therefore, the white portion of the first facing surface 62 shown in FIG. 5 without dot hatching is the sliding surface 65 on which the plurality of pressure receiving portions 75 slide when the movable scroll 32 revolves. The first facing surface 62 has a plurality of sliding surfaces 65. The plurality of sliding surfaces 65 are arranged at intervals in the circumferential direction of the first thrust bearing plate 61.

The non-sliding surface 66 has a plurality of first non-sliding surfaces 661 provided at positions where the movable scroll 32 overlaps with each insertion hole 74 in the axial direction when the movable scroll 32 revolves. A plurality of first non-sliding surfaces 661 are arranged at equal intervals in the circumferential direction of the first thrust bearing plate 61. Each of the first non-sliding surfaces 661 is arranged between the sliding surfaces 65 adjacent to each other in the circumferential direction of the first thrust bearing plate 61.

In FIG. 5, among the portions of the first facing surface 62 that are dot-hatched, the portion that is not shaded is the first non-sliding surface 661. Here, in FIG. 5, the locus of the position of the first thrust bearing plate 61 with respect to the first facing surface 62 in each insertion hole 74 when the movable scroll 32 revolves is shown by a virtual circle. Then, in FIG. 5, when the movable scroll 32 revolves, the locus of the position of the first thrust bearing plate 61 at the portion most distant from each pin 64 in each insertion hole 74 with respect to the first facing surface 62 is a virtual circle C2. It is shown by. As shown in FIG. 5, each first non-sliding surface 661 is a region located inside each virtual circle C2. Therefore, each of the first non-sliding surfaces 661 overlaps with each of the insertion holes 74 in the axial direction of the rotating shaft 12 when the movable scroll 32 revolves among the non-sliding surfaces 66, and a plurality of pressure receiving portions. 75 is a non-sliding part. Therefore, the non-sliding surface 66 partially overlaps with each insertion hole 74 when the movable scroll 32 revolves.

A part of each first non-sliding surface 661 is provided at a position on the outer peripheral side in the radial direction with respect to each sliding surface 65. Therefore, when the movable scroll 32 revolves, a part of each first non-sliding surface 661 is provided on the first facing surface 62 at a position on the outer peripheral side in the radial direction with respect to each sliding surface 65. As described above, the protruding positions of the plurality of pressure receiving portions 75 with respect to the second facing surface 72 and the size of the hole diameter of each insertion hole 74 are preset.

Further, the non-sliding surface 66 is provided at a position where the movable scroll 32 does not overlap with each insertion hole 74 when the movable scroll 32 revolves and is on the outer peripheral side in the radial direction with respect to each sliding surface 65. It has a plurality of non-sliding surfaces 662. Therefore, a part of the non-sliding surface 66 is provided at a position where the movable scroll 32 does not overlap with each insertion hole 74 when it revolves and is on the outer peripheral side in the radial direction with respect to the sliding surface 65. .. In FIG. 5, among the portions of the first facing surface 62 that are dot-hatched, the portion that is shaded and is on the outer peripheral side in the radial direction with respect to each sliding surface 65. The second non-sliding surface 662. Each of the second non-sliding surfaces 662 extends in an arc shape along the outer peripheral edge portion of the first facing surface 62 between the first non-sliding surfaces 661 adjacent to each other in the circumferential direction of the first thrust bearing plate 61. .. Each of the second non-sliding surfaces 662 connects the first non-sliding surfaces 661 adjacent to each other in the circumferential direction of the first thrust bearing plate 61.

Further, the non-sliding surface 66 has a plurality of third non-sliding surfaces 663 that do not overlap with the insertion holes 74 when the movable scroll 32 revolves and are located on the inner peripheral side of the virtual circle C2. ing. In FIG. 5, among the parts of the first facing surface 62 that are dot-hatched, the part that is shaded and is located on the inner peripheral side of the virtual circle C2 is the third non-third part. The sliding surface 663. Each third non-sliding surface 663 extends along the inner peripheral edge portion of the first facing surface 62 between the sliding surfaces 65 adjacent to each other in the circumferential direction of the first thrust bearing plate 61.

As shown in FIG. 4, the first thrust bearing plate 61 has a flat plate main body portion 67 and a coating layer 68 coated on one surface of the plate main body portion 67. The plate body 67 is made of, for example, steel. The first thrust bearing plate 61 is fixed to the movable scroll 32 by joining the surface of the plate body 67 opposite to the coating layer 68 to the back surface 32e of the movable substrate 32a. Therefore, the first facing surface 62 of the first thrust bearing plate 61 is made of a coating layer 68.

The coating layer 68 is provided on one surface of the plate body 67 in a state of covering one surface of the plate body 67 by applying a resin coating to one surface of the plate body 67. The coating layer 68 is formed by adding a solid lubricant to the binder resin. Examples of the binder resin include polyamide-imide-based resins, polyimide-based resins, or diisocyanate-modified resins, BPDA-modified resins, sulfone-modified resins, epoxy resins, phenol resins, polyamides, estramers, and acrylate compounds (methacrylate compounds) of these resins. And so on. Examples of the solid lubricant include graphite, carbon, molybdenum disulfide, polytetrafluoroethylene, boron nitride, tungsten disulfide, a fluororesin, and soft metals such as Sn and Bi. The coating layer 68 is formed of a soft material having a Vickers hardness that is 100 or more lower than the Vickers hardness of each pressure receiving portion 75 of the second thrust bearing plate 71.

The sliding surface 65 has a smooth surface 65a and a plurality of sliding surface grooves 65b recessed from the smooth surface 65a. The smooth surface 65a is a flat surface extending along the flat surface 75f of each pressure receiving portion 75. The sliding surface groove 65b is streaky. Further, the non-sliding surface 66 has a plurality of non-sliding surface grooves 66b. The non-sliding surface groove 66b is streaky. The surface roughness of the non-sliding surface 66 is 10 μm to 20 μm. The surface roughness of the sliding surface 65 is 5 μm or less. Therefore, the surface roughness of the non-sliding surface 66 is larger than the surface roughness of the sliding surface 65.

As shown in FIG. 6, the surface roughness of the coating layer 68 formed by applying the resin coating to one surface of the plate main body 67 is 10 μm to 20 μm. Then, the first thrust bearing plate 61 is fixed to the back surface 32e of the movable substrate 32a while leaving the surface roughness of the coating layer 68 as the initial roughness of the first facing surface 62.

As shown in FIG. 7, when the movable scroll 32 revolves, the plurality of pressure receiving portions 75 slide on the first facing surface 62, so that the sliding surface 65 is formed on the first facing surface 62. At this time, the flat surface 75f of each pressure receiving portion 75 slides on the first facing surface 62, and the first facing surface 62 is scraped and smoothed by the flat surface 75f of each pressure receiving portion 75, whereby the sliding surface is smoothed. A smooth surface 65a is formed on the 65. In this way, the sliding surface 65 is smoothed by the flat surface 75f of each pressure receiving portion 75, so that the surface roughness is smaller than the initial roughness of the first facing surface 62.

As shown in FIG. 8, a portion of the sliding surface 65 that remains as the initial roughness of the first facing surface 62 without being scraped by the flat surface 75f of each pressure receiving portion 75 when the movable scroll 32 revolves. Exists as a sliding surface groove 65b that is recessed from the smooth surface 65a. Therefore, the initial roughness of the first facing surface 62 is such that the sliding surface groove 65b slides even if the first facing surface 62 is scraped by the flat surface 75f of each pressure receiving portion 75 when the movable scroll 32 revolves. The surface roughness is set so as to exist on the surface 65.

Further, when the movable scroll 32 revolves, a portion of the first facing surface 62 where the plurality of pressure receiving portions 75 do not slide is formed as the non-sliding surface 66. Therefore, the surface roughness of the non-sliding surface 66 is the same as the initial roughness of the first facing surface 62. The surface roughness of each of the first non-sliding surface 661, each second non-sliding surface 662, and each third non-sliding surface 663 is the same, and the first non-sliding surface 661 and the second non-sliding surface 661 are the same. Non-sliding surface grooves 66b are formed on each of the surface 662 and the third non-sliding surface 663.

As shown in FIG. 5, each of the first non-sliding surfaces 661 overlaps with each insertion hole 74 in the axial direction of the rotation shaft 12 and a plurality of the first non-sliding surfaces 661 on the first facing surface 62 when the movable scroll 32 revolves. The pressure receiving portion 75 is formed in a portion where the pressure receiving portion 75 does not slide. Therefore, each first non-sliding surface 661 is inevitably formed on the first facing surface 62 due to the presence of each insertion hole 74 when the movable scroll 32 revolves.

Further, each second non-sliding surface 662 does not overlap with each insertion hole 74 when the movable scroll 32 revolves on the first facing surface 62, and is radially outer peripheral side with respect to each sliding surface 65. It is provided at the position where. Therefore, when the movable scroll 32 revolves, a plurality of pressure receiving portions 75 are located on the first facing surface 62 so as not to overlap with each insertion hole 74 and to be on the outer peripheral side in the radial direction with respect to each sliding surface 65. The protruding positions of the plurality of pressure receiving portions 75 with respect to the second facing surface 72, the size of the hole diameter of each insertion hole 74, and the size of the outer diameter of the first thrust bearing plate 61 are determined in advance so that It is set.

Further, each third non-sliding surface 663 is a portion of the first facing surface 62 that does not overlap with each insertion hole 74 when the movable scroll 32 revolves and is located on the inner peripheral side of the virtual circle C2. Is formed in. Therefore, when the movable scroll 32 revolves, a plurality of pressure receiving portions 75 slide on the first facing surface 62 at a portion that does not overlap with each insertion hole 74 and is located on the inner peripheral side of the virtual circle C2. To prevent this, the protruding positions of the plurality of pressure receiving portions 75 with respect to the second facing surface 72, the size of the hole diameter of each insertion hole 74, and the size of the hole diameter of the first through hole 63 of the first thrust bearing plate 61. Is preset.

As shown in FIG. 4, since the surface roughness of the non-sliding surface 66 is larger than the surface roughness of the sliding surface 65, the non-sliding surface per unit area formed with respect to the non-sliding surface 66. The amount of the groove 66b is larger than the amount of the sliding surface groove 65b per unit area formed with respect to the sliding surface 65.

Next, the operation of this embodiment will be described.
The movable scroll 32 receives a thrust load due to the pressure difference between the pressure of the refrigerant compressed by the revolving motion of the movable scroll 32 and the pressure of the back pressure chamber 54 acting on the back surface 32e of the movable substrate 32a of the movable scroll 32. .. In particular, in the scroll type compressor 10 that uses carbon dioxide as the refrigerant that is the fluid to be compressed, the pressure of the compressed refrigerant is high, so that the thrust load received by the movable scroll 32 becomes large.

Here, the oil contained in the refrigerant of the back pressure chamber 54 is supplied between the first facing surface 62 and the second facing surface 72. Then, the oil supplied between the first facing surface 62 and the second facing surface 72 is formed from the periphery of each pressure receiving portion 75 to the flat surface of each pressure receiving portion 75 due to the wedge effect of the chamfered portion 75e of each pressure receiving portion 75. It is drawn between the 75f and each sliding surface 65 of the first facing surface 62, and an oil film is formed between the flat surface 75f of each pressure receiving portion 75 and the smooth surface 65a of each sliding surface 65. The thrust bearing portion 60 receives the thrust load from the movable scroll 32 on the shaft support member 20 side by the reaction force of the oil film formed between the flat surface 75f of each pressure receiving portion 75 and the smooth surface 65a of each sliding surface 65. Accept at. Further, the oil film formed between the flat surface 75f of each pressure receiving portion 75 and the smooth surface 65a of each sliding surface 65 makes it difficult for friction between each pressure receiving portion 75 and the first facing surface 62 to occur. As a result, the lubricity of the thrust bearing portion 60 is maintained, and seizure between each sliding surface 65 of the first facing surface 62 and the flat surface 75f of each pressure receiving portion 75 is suppressed.

Further, the oil supplied between the first facing surface 62 and the second facing surface 72 is held in the non-sliding surface groove 66b of the non-sliding surface 66. Further, the oil drawn from the periphery of each pressure receiving portion 75 between the flat surface of each pressure receiving portion 75 and each sliding surface 65 is held in the sliding surface groove 65b of each sliding surface 65.

Here, the oil held in the non-sliding surface groove 66b of the non-sliding surface 66 is affected by the centrifugal force accompanying the revolution movement of the movable scroll 32, and is held in the non-sliding surface groove 66b. Is blown off from the non-sliding surface groove 66b by centrifugal force. As a result, the oil held in the non-sliding surface groove 66b is supplied between the flat surface 75f of each pressure receiving portion 75 and each sliding surface 65, and each sliding with the flat surface 75f of each pressure receiving portion 75. An oil film is likely to be formed between the smooth surface 65a of the surface 65. Therefore, the lubricity of the thrust bearing portion 60 is further improved.

Further, the centrifugal force accompanying the revolution movement of the movable scroll 32 also acts on the oil held in the sliding surface groove 65b of each sliding surface 65, and the oil held in each sliding surface groove 65b is centrifugal. It is blown off from each sliding surface groove 65b by the force. As a result, the oil held in each sliding surface groove 65b is also supplied between the flat surface 75f of each pressure receiving portion 75 and each sliding surface 65, and each sliding with the flat surface 75f of each pressure receiving portion 75. An oil film is likely to be formed between the smooth surface 65a of the surface 65. Therefore, the lubricity of the thrust bearing portion 60 is further improved.

Further, the centrifugal force accompanying the revolution movement of the movable scroll 32 acts on the oil between the flat surface 75f of each pressure receiving portion 75 and each sliding surface 65, and the radial outer peripheral side with respect to each sliding surface 65. Even if the oil is blown off, the oil is provided by a part of each first non-sliding surface 661 or each second non-sliding surface 662 provided at a position on the outer peripheral side in the radial direction with respect to each sliding surface 65. Is retained. Therefore, a part of each first non-sliding surface 661 and the oil held on each second non-sliding surface 662 revolve with the revolving motion of the movable scroll 32, and the flat surface 75f of each pressure receiving portion 75 and each sliding. It becomes easy to be supplied between the moving surface 65 and the moving surface 65. As a result, the lubricity of the thrust bearing portion 60 is further improved.

In the above embodiment, the following effects can be obtained.
(1) Since the surface roughness of the non-sliding surface 66 is larger than the surface roughness of the sliding surface 65, for example, the surface roughness of the non-sliding surface 66 on the first facing surface 62 is the sliding surface 65. The amount of oil held on the non-sliding surface 66 can be increased as compared with the case where the surface roughness is less than or equal to that of. Specifically, since the surface roughness of the non-sliding surface 66 is larger than the surface roughness of the sliding surface 65, the non-sliding surface groove 66b per unit area formed with respect to the non-sliding surface 66. The amount of is larger than the amount of the sliding surface groove 65b per unit area formed with respect to the sliding surface 65. Therefore, the amount of oil per unit area held in the non-sliding surface groove 66b of the non-sliding surface 66 is the amount of oil per unit area held in the sliding surface groove 65b of the sliding surface 65. Is more than. Therefore, the oil held on the non-sliding surface 66 is easily supplied between each pressure receiving portion 75 and the sliding surface 65 as the movable scroll 32 revolves, and each pressure receiving portion 75 and the sliding surface are easily supplied. An oil film is likely to be formed between 65 and 65. As a result, for example, even when the scroll type compressor 10 is operated in a situation where it is difficult to supply oil between the first facing surface 62 and the second facing surface 72, the pressure receiving portions 75 An oil film can be easily formed between the first facing surface 62 and the thrust bearing portion 60, and the lubricity of the thrust bearing portion 60 can be improved.

(2) The first facing surface 62 revolves together with the movable scroll 32, and the second facing surface 72 is fixed to the shaft support member 20. According to this, the centrifugal force accompanying the revolution movement of the movable scroll 32 acts on the oil held on the non-sliding surface 66, and the oil held on the non-sliding surface 66 is non-sliding due to the centrifugal force. It becomes easy to be blown off from the moving surface 66. As a result, the oil held on the non-sliding surface 66 is easily supplied between each pressure receiving portion 75 and the sliding surface 65, so that an oil film is formed between each pressure receiving portion 75 and the sliding surface 65. It becomes easy to be formed. Therefore, the lubricity of the thrust bearing portion 60 can be further improved.

(3) A part of the non-sliding surface 66 is provided at a position on the outer peripheral side in the radial direction with respect to the sliding surface 65. According to this, the centrifugal force due to the revolution movement of the movable scroll 32 acts on the oil between each pressure receiving portion 75 and the sliding surface 65, and the oil is discharged to the outer peripheral side in the radial direction with respect to the sliding surface 65. Even if it is blown off, the oil can be held by the non-sliding surface 66 provided at a position on the outer peripheral side in the radial direction with respect to the sliding surface 65. Therefore, the oil held on the non-sliding surface 66 is easily supplied between each pressure receiving portion 75 and the sliding surface 65 as the movable scroll 32 revolves, and each pressure receiving portion 75 and the sliding surface are easily supplied. An oil film is likely to be formed between 65 and 65. As a result, the lubricity of the thrust bearing portion 60 can be further improved.

(4) Each second non-sliding surface 662, which is a part of the non-sliding surface 66, does not overlap with each insertion hole 74 when the movable scroll 32 revolves, and has a diameter with respect to the sliding surface 65. It is provided at a position on the outer peripheral side in the direction. According to this, for example, the non-sliding surface 66 is formed only at a portion of the first facing surface 62 that overlaps with each insertion hole 74 in the axial direction when the movable scroll 32 revolves. The region of the non-sliding surface 66 on the first facing surface 62 can be increased as compared with the case where the above is performed. Therefore, since the amount of oil held on the non-sliding surface 66 increases, the oil held on the non-sliding surface 66 is more likely to be supplied between each pressure receiving portion 75 and the sliding surface 65. , An oil film is more likely to be formed between each pressure receiving portion 75 and the sliding surface 65. As a result, the lubricity of the thrust bearing portion 60 can be further improved.

(5) The non-sliding surface 66 having a surface roughness of 10 μm to 20 μm is suitable as the non-sliding surface 66 for holding oil. Further, the sliding surface 65 having a surface roughness of 5 μm or less is suitable as the sliding surface 65 for forming an oil film between each pressure receiving portion 75 and the sliding surface 65.

(6) Each first non-sliding surface 661 is inevitably formed on the first facing surface 62 due to the presence of each insertion hole 74 when the movable scroll 32 revolves. Therefore, since each first non-sliding surface 661 is automatically formed on the first facing surface 62 by using each insertion hole 74 constituting the rotation preventing mechanism 80 that prevents the movable scroll 32 from rotating, the first non-sliding surface 661 is automatically formed. Each first non-sliding surface 661 can be easily formed on one facing surface 62.

(7) On the sliding surface 65, when the movable scroll 32 revolves, a portion that is not scraped by the flat surface 75f of each pressure receiving portion 75 and remains as the initial roughness of the first facing surface 62 is the smooth surface 65a. It exists as a sliding surface groove 65b that is recessed more than the above. Therefore, the sliding surface groove 65b can be automatically formed on the sliding surface 65. Then, the centrifugal force accompanying the revolution movement of the movable scroll 32 acts on the oil held in the sliding surface groove 65b of each sliding surface 65, and the oil held in each sliding surface groove 65b has a centrifugal force. Is blown away from each sliding surface groove 65b. As a result, the oil held in each sliding surface groove 65b is supplied between the flat surface 75f of each pressure receiving portion 75 and each sliding surface 65, and each sliding with the flat surface 75f of each pressure receiving portion 75. An oil film is likely to be formed between the smooth surface 65a of the surface 65. Therefore, the lubricity of the thrust bearing portion 60 can be further improved.

(8) As the coating layer 68, for example, a diamond-like carbon layer may be adopted. According to this, for example, the scroll type compressor 10 is operated under a situation where it is difficult to supply oil between the first facing surface 62 and the second facing surface 72, and each pressure receiving portion 75 and the first facing surface are operated. Even when it is difficult to form an oil film between the pressure receiving portion 75 and the first facing surface 62, friction between the pressure receiving portions 75 and the first facing surface 62 is unlikely to occur. However, in the diamond-like carbon layer, if the surface treatment of the surface of the base material to be coated is not performed accurately, the diamond-like carbon layer may be peeled off from the surface of the base material, so that the coating treatment is costly. .. In the present embodiment, even when the scroll type compressor 10 is operated in a situation where it is difficult to supply oil between the first facing surface 62 and the second facing surface 72, each pressure receiving unit 75 and the first Since an oil film is likely to be formed between the facing surface 62 and the facing surface 62, it is not necessary to use a diamond-like carbon layer as the coating layer 68 on the surface of the first facing surface 62. Therefore, the cost can be reduced.

(9) Since the first thrust bearing plate 61 revolves with respect to the second thrust bearing plate 71, for example, when the rotation speed of the rotating shaft 12 is constant, the first thrust bearing plate with respect to the second thrust bearing plate 71 The rotation speed (revolution speed) of 61 is slower than the rotation speed of the rotation shaft 12 for each of the thrust bearings 19 and 23. As the rotation speed of the first thrust bearing plate 61 with respect to the second thrust bearing plate 71 becomes slower, between the periphery of each pressure receiving portion 75 and the flat surface 75f of each pressure receiving portion 75 and each sliding surface 65 of the first facing surface 62. It becomes difficult for oil to be drawn into the surface, and it becomes difficult for an oil film to be formed between the flat surface 75f of each pressure receiving portion 75 and the smooth surface 65a of each sliding surface 65. Therefore, in the scroll type compressor 10, the amount of oil supplied between the first facing surface 62 and the second facing surface 72 is the amount of oil supplied between the slide bearings 19 and 23 and the rotary shaft 12. Tends to be less than the amount of. Therefore, in the present embodiment, the oil held in the non-sliding surface groove 66b is supplied between the flat surface 75f of each pressure receiving portion 75 and each sliding surface 65, and the flat surface 75f of each pressure receiving portion 75 is supplied. Since it is easy to form an oil film between the sliding surface 65 and the smooth surface 65a of each sliding surface 65, it is possible to easily maintain the lubricity in the thrust bearing portion 60 of the scroll type compressor 10.

The above embodiment can be modified and implemented as follows. The above embodiment and the following modified examples can be implemented in combination with each other within a technically consistent range.

○ In the embodiment, in the thrust bearing portion 60, the first thrust bearing plate 61 is fixed to the end face of the shaft support member 20 opposite to the motor chamber 22, and the second thrust bearing plate 71 is movable of the movable scroll 32. The configuration may be fixed to the back surface 32e of the substrate 32a. In this case, on the first facing surface 62, the oil held in the non-sliding surface groove 66b of the non-sliding surface 66 follows the refrigerant around each pressure receiving portion 75 flowing out with the revolution movement of the movable scroll 32. Then, it is drawn out from the non-sliding surface groove 66b and supplied between the flat surface 75f of each pressure receiving portion 75 and each sliding surface 65. As a result, an oil film is likely to be formed between the flat surface 75f of each pressure receiving portion 75 and the smooth surface 65a of each sliding surface 65. Therefore, the lubricity of the thrust bearing portion 60 is further improved. In short, one of the first facing surface 62 and the second facing surface 72 may revolve together with the movable scroll 32, and the other of the first facing surface 62 and the second facing surface 72 may be fixed to the shaft support member 20. ..

○ In the embodiment, the thrust bearing portion 60 may be configured not to include the first thrust bearing plate 61 and the second thrust bearing plate 71. In this case, the thrust bearing portion 60 has, for example, the back surface 32e of the movable substrate 32a of the movable scroll 32 as the first facing surface 62, and the end surface of the shaft support member 20 opposite to the motor chamber 22 as the second facing surface 72. It may be configured to be.

○ In the embodiment, the non-sliding surface 66 may have a configuration that does not have the second non-sliding surface 662 and the third non-sliding surface 663. That is, only the first non-sliding surface 661 may be formed on the first facing surface 62 as the non-sliding surface 66. In short, the first facing surface 62 is provided at a position where at least a part thereof overlaps with each insertion hole 74 in the axial direction when the movable scroll 32 revolves, and a plurality of pressure receiving portions 75 slide. It suffices to have a non-sliding surface 66 that does not move.

○ In the embodiment, the non-sliding surface 66 may have a configuration that does not have the third non-sliding surface 663.
○ In the embodiment, the non-sliding surface 66 may have a configuration that does not have the second non-sliding surface 662. In this case, only a part of each first non-sliding surface 661 is provided on the first facing surface 62 at a position on the outer peripheral side in the radial direction with respect to each sliding surface 65.

○ In the embodiment, all the portions of each first non-sliding surface 661 may be provided on the first facing surface 62 at a position on the outer peripheral side in the radial direction with respect to each sliding surface 65. In short, at least a part of the non-sliding surface 66 may be provided on the first facing surface 62 at a position on the outer peripheral side in the radial direction with respect to each sliding surface 65.

○ In the embodiment, the non-sliding surface 66 may have a configuration that does not have the second non-sliding surface 662. Further, a part of each first non-sliding surface 661 may not be provided on the first facing surface 62 at a position on the outer peripheral side in the radial direction with respect to each sliding surface 65. In short, the non-sliding surface 66 may not be provided on the first facing surface 62 at a position on the outer peripheral side in the radial direction with respect to each sliding surface 65.

○ In the embodiment, the coating layer 68 is provided on one surface of the plate body 67 in a state of covering one surface of the plate body 67 by, for example, applying a soft metal coating to one surface of the plate body 67. May be. Examples of the soft metal coating include Sn plating, Cu plating, Zn plating, Bi plating and the like. In short, the coating layer 68 may be formed of a material that is soft with respect to the Vickers hardness of each pressure receiving portion 75 of the second thrust bearing plate 71.

○ In the embodiment, the surface roughness of the non-sliding surface 66 may be in the range of 3 μm to 20 μm. For example, when the surface roughness of the non-sliding surface 66 is 3 μm, the surface roughness of the sliding surface 65 may be less than 3 μm. In short, the surface roughness of the non-sliding surface 66 may be larger than the surface roughness of the sliding surface 65.

○ In the embodiment, each pressure receiving portion 75 does not have to be a columnar shape, and may be, for example, a triangular columnar column or a square columnar shape. Even in this case, the tip surface of each pressure receiving portion 75 has a flat surface shape, and the entire peripheral edge portion which is a corner portion between the outer peripheral surface 75a and the flat surface 75f of each pressure receiving portion 75 is chamfered. Must be.

O In the embodiment, the chamfered portion 75e of each pressure receiving portion 75 may not be chamfered in an arc shape, and may be, for example, a conical tapered shape chamfered in a conical shape. In short, at the peripheral edge of each pressure receiving portion 75, the entire peripheral edge, which is a corner portion between the outer peripheral surface 75a and the flat surface 75f of each pressure receiving portion 75, may be chamfered so that a wedge effect can be obtained. ..

O In the embodiment, the number of pins 64 protruding from the first facing surface 62 may be two or more. In short, the number of pins 64 protruding from the first facing surface 62 may be a plurality, and each of them is inserted into the insertion holes 74 formed in the second facing surface 72 to prevent the movable scroll 32 from rotating. Anything that constitutes the mechanism 80 may be used. It is necessary to appropriately change the number of insertion holes 74 formed in the second facing surface 72 according to the number of pins 64 protruding from the first facing surface 62.

O In the embodiment, the second facing surface 72 may be formed with an insertion recess as an insertion portion into which a plurality of pins 64 are inserted. In short, the insertion portion into which the pin 64 is inserted is not limited to the insertion hole 74 that penetrates the second thrust bearing plate 71 in the thickness direction.

○ In the embodiment, the facing member arranged on the side opposite to the fixed scroll 31 with respect to the movable scroll 32 is not limited to the shaft support member 20. For example, a member that functions as an opposing member may be separately arranged between the movable scroll 32 and the shaft support member 20.

○ In the embodiment, for example, rolling bearings may be adopted instead of the sliding bearings 19 and 23, respectively.
○ In the embodiment, the scroll type compressor 10 may have a configuration in which the peripheral wall 15b of the motor housing 15 does not cover the compression mechanism 13 on the radial outside of the rotating shaft 12. For example, the fixed outer peripheral wall 31c of the fixed scroll 31 may form a part of the housing 11.

○ In the embodiment, the scroll type compressor 10 may have, for example, a configuration in which the inverter device 18 is arranged radially outside the rotation shaft 12 with respect to the housing 11. In short, the compression mechanism 13, the electric motor 14, and the inverter device 18 do not have to be arranged side by side in the axial direction of the rotating shaft 12 in this order.

○ In the embodiment, the scroll type compressor 10 does not have to be the type driven by the electric motor 14, and may be, for example, the type driven by the engine of the vehicle.

-In the embodiment, carbon dioxide is adopted as the refrigerant, but for example, Freon may be adopted as the refrigerant.
○ In the embodiment, the scroll type compressor 10 is used in a vehicle air conditioner, but the present invention is not limited to this. For example, the scroll type compressor 10 is mounted on a fuel cell vehicle and is supplied to a fuel cell. It may be used to compress air as a fluid by the compression mechanism 13.

10 ... Scroll type compressor, 20 ... Shaft support member which is an opposed member, 31 ... Fixed scroll, 32 ... Movable scroll, 60 ... Thrust bearing portion, 62 ... First facing surface, 64 ... Pin, 65 ... Sliding surface, 66 ... non-sliding surface, 68 ... coating layer, 72 ... second facing surface, 74 ... insertion hole as an insertion part, 75 ... pressure receiving part, 80 ... rotation prevention mechanism.

Claims (5)

Fixed scroll and
A movable scroll that is placed facing the fixed scroll and that compresses the fluid by revolving with respect to the fixed scroll in a state where the rotation is prevented by the rotation prevention mechanism.
An opposing member arranged on the opposite side of the fixed scroll with respect to the movable scroll,
A thrust bearing portion that receives a thrust load from the movable scroll on the facing member side is provided.
The thrust bearing portion is formed with a first facing surface made of a coating layer and a plurality of pressure receiving portions facing the first facing surface and projecting toward the first facing surface and sliding on the first facing surface. With a second facing surface,
A plurality of pins constituting the rotation prevention mechanism are projected on the first facing surface.
An insertion portion into which the plurality of pins are inserted is formed on the second facing surface.
One of the first facing surface and the second facing surface revolves together with the movable scroll, and the other of the first facing surface and the second facing surface is fixed to the facing member.
The first facing surface is a sliding surface on which the plurality of pressure receiving portions slide when the movable scroll revolves, and a non-sliding surface on which the plurality of pressure receiving portions do not slide when the movable scroll revolves. With a moving surface,
The non-sliding surface is provided at a position where at least a part thereof overlaps with each of the insertion portions in the axial direction.
A scroll type compressor in which the surface roughness of the non-sliding surface is larger than the surface roughness of the sliding surface. The scroll type compressor according to claim 1, wherein the first facing surface revolves together with the movable scroll, and the second facing surface is fixed to the facing member. The scroll type compressor according to claim 1 or 2, wherein at least a part of the non-sliding surface is provided at a position on the outer peripheral side in the radial direction with respect to the sliding surface. A claim that a part of the non-sliding surface is provided at a position where the movable scroll does not overlap with each of the insertion portions when the movable scroll revolves and is on the outer peripheral side in the radial direction with respect to the sliding surface. The scroll type compressor according to any one of claims 1 to 3. The surface roughness of the non-sliding surface is 10 μm to 20 μm.
The scroll type compressor according to any one of claims 1 to 4, wherein the surface roughness of the sliding surface is 5 μm or less.

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