JP7206084B2 - scroll compressor - Google Patents

Description

The present invention relates to scroll compressors.

The scroll compressor includes a main shaft rotationally driven by an electric motor, an eccentric shaft provided at a position offset from the main shaft, an orbiting scroll supported by the eccentric shaft, and a volume variable by facing the orbiting scroll. and a fixed scroll forming a compression chamber of. The orbiting scroll revolves around the axis of the main shaft without rotating. This compresses the fluid introduced into the compression chamber. As a specific example of such a scroll compressor, one described in Patent Document 1 below is known.

Here, the scroll compressor as described above requires lubricating oil for lubricating the bearing device that rotatably supports the main shaft. A small amount of the lubricating oil also flows out of the scroll compressor along with the flow of the refrigerant. If the amount of lubricating oil discharged outside together with the refrigerant increases, the heat exchange efficiency of the refrigeration system may decrease. On the other hand, in order to improve heat exchange efficiency, it is necessary to reduce the amount of lubricating oil that flows together with the refrigerant. However, when the oil circulation rate decreases, it becomes difficult to ensure lubrication performance in the bearing device.

On the other hand, it is conceivable to divide the space in which the compression chamber is formed from the space in which the bearing device and the electric motor are arranged, and divide the path through which the refrigerant flows from the path through which the lubricating oil flows. Specifically, the space in the housing is partitioned by the bearing device, and the bearing device and the electric motor are accommodated in the space on one side (mechanical space), and the orbiting scroll and the fixed scroll are accommodated in the space on the other side (suction space). do.

JP 2016-223351 A

However, in the above configuration, due to the differential pressure between the suction space and the mechanical space, lubricating oil may flow into the suction space through a minute gap formed between the rotating shaft and the bearing device. . As a result, the refrigerant may be mixed with other fluids including lubricating oil, and the thermal conductivity of the refrigerant may decrease.

SUMMARY OF THE INVENTION An object of the present invention is to provide a scroll compressor capable of reducing the amount of other fluid mixed into refrigerant.

According to a first aspect of the present invention, a scroll compressor includes a rotating shaft that extends along an axis and rotates about the axis, a bearing device that rotatably supports the rotating shaft, and a rotating shaft that rotates the rotating shaft. a drive unit for driving; a compression unit arranged on the opposite side of the drive unit in the axial direction in which the axis extends across the bearing device, and for compressing a refrigerant by being rotated by the rotating shaft; a housing that accommodates a driving portion and a compression portion and stores therein lubricating oil for lubricating the bearing device; a suction pipe for supplying a coolant, wherein the outer peripheral surface of the bearing device is fixed in contact with the inner peripheral surface of the housing over the entire circumference, and the compression portion extends from the bearing device side in the axial direction. has a compression portion seal surface facing the opposite side, and is provided eccentrically with respect to the axis so as to revolve around the axis; and a compression portion facing the compression portion seal surface in the axial direction. A fixed scroll having a facing surface and forming a compression chamber for compressing a refrigerant between itself and the orbiting scroll is provided between the compression section sealing surface and the compression section facing surface to seal the flow of fluid. and a sealing portion, wherein the fixed scroll includes a disk-shaped end plate centered on the axis, a spiral fixed wrap provided on one side of the end plate in the axial direction, and the fixed wrap. The compression section facing surface is a surface of the outer peripheral wall facing the orbiting scroll side, and a part of the outer peripheral wall has a communication hole penetrating in the radial direction is formed, and the communication hole is formed right beside the opening of the suction pipe so that the position in the axial direction overlaps with the connection portion between the suction pipe and the housing, and the refrigerant flowing in from the suction pipe is supplied only to the compression portion through the communication hole without passing around the drive portion and the bearing device in the housing, and the seal portion is provided on the compression portion facing surface and the compression portion seal A surface that contacts at least one of the surfaces is coated with DLC .

According to this configuration, since the sealing portion is provided, the flow of fluid between the orbiting scroll and the fixed scroll is sealed between the compression portion sealing surface and the compression portion facing surface. As a result, it is possible to reduce the possibility that fluid other than the refrigerant (for example, lubricating oil) will flow into the compression chamber. That is, it is possible to avoid a decrease in heat capacity caused by mixing other fluids with the refrigerant.
A surface of the outer peripheral wall of the fixed scroll facing toward the orbiting scroll serves as a surface facing the compression portion, and a seal portion is provided between the surface facing the compression portion and the seal surface of the compression portion. This prevents the seal from interfering with other components including, for example, Oldham's rings and thrust plates. Therefore, there is no need to secure an area for providing the seal portion by avoiding other components, and the diameter of the fixed scroll and the orbiting scroll can be reduced. As a result, it is possible to further reduce the amount of fluid that flows into the compression chamber through the space between the compression portion sealing surface and the compression portion facing surface. That is, it is possible to further reduce the decrease in heat capacity caused by mixing the refrigerant with other fluids.

According to another aspect of the present invention, at least one of the compression portion sealing surface and the compression portion opposing surface is formed with an accommodation groove recessed in the axial direction so as to accommodate a portion of the seal portion. ,
The seal portion may protrude in the axial direction from the accommodation groove.

According to this configuration, since the seal portion is accommodated in the accommodation groove, it is possible to prevent the seal portion from coming off or being displaced during operation of the scroll compressor. Furthermore, since the seal portion protrudes from the accommodation groove in the axial direction, only the seal portion can be brought into close contact with the compression portion sealing surface and the compression portion facing surface. As a result, it is possible to more effectively seal the circulation of the fluid while allowing the orbiting scroll to revolve more smoothly.

According to another aspect of the invention, the seal portion may have an annular shape centered on the axis.

According to this configuration, since the seal portion has an annular shape centered on the axis, it is possible to surround the compression chamber from the outer peripheral side with respect to the axis without a gap. As a result, it is possible to further reduce the amount of fluid that flows into the compression chamber through the space between the compression portion sealing surface and the compression portion facing surface.

According to another aspect of the present invention, the seal portion includes a seal portion main body that abuts against one of the compression portion seal surface and the compression portion facing surface, and a seal portion main body that includes the compression portion seal surface and the compression portion. and an elastic portion that biases toward one of the opposing surfaces.

According to this configuration, since the elastic portion urges the seal portion body toward one of the compression portion sealing surface and the compression portion facing surface, the seal portion main body and one of the compression portion sealing surface and the compression portion facing surface can more effectively reduce fluid leakage between Furthermore, even if the main body of the sealing portion wears out due to long-term use, the elastic portion continues to urge the sealing portion toward one of the sealing surface of the compression portion and the surface facing the compression portion. can.

ADVANTAGE OF THE INVENTION According to this invention, the scroll compressor which can reduce the mixing amount of the other fluids to a refrigerant|coolant can be provided.

1 is a longitudinal sectional view of a scroll compressor according to an embodiment of the invention; FIG. 4 is an enlarged view of a seal portion according to the embodiment of the present invention; FIG. It is a top view of the seal part concerning the embodiment of the present invention.

An embodiment of the present invention will be described with reference to FIGS. 1 to 4. FIG. As shown in FIG. 1, the scroll compressor 100 includes a housing 1 forming the outer shape of the apparatus, a drive section 3 (electric motor 3) provided in the housing 1, and a rotating shaft 4 rotated by the drive section 3. , a compression unit 2 driven by the rotation of the rotating shaft 4, a main bearing 9A (bearing device 9A) that rotatably supports the rotating shaft 4, and a sub-bearing 9B.

The compressing portion 2 and the driving portion 3 are connected to each other by a rotating shaft 4 extending along the axis O1. That is, the rotational energy generated by the driving section 3 is immediately transmitted to the compressing section 2 through the rotating shaft 4 . The compression part 2 compresses the refrigerant gas (refrigerant) as a working fluid by this rotational energy and discharges it to the outside in a high pressure state. High-pressure refrigerant gas is used, for example, as a refrigerant in air conditioners and the like. The configuration of each unit will be described in detail below.

The housing 1 is provided with a suction pipe 11 for sucking refrigerant gas as a working fluid from the outside, and a discharge pipe 12 for discharging the refrigerant gas that has been compressed by the compression section 2 and is in a high pressure state. Lubricating oil for lubricating a main bearing 9A and a sub-bearing 9B, which will be described later, is stored in the lower part of the housing 1 . The lubricating oil is supplied to the lower portion of the housing 1 via a lubricating oil supply pipe (not shown).

The rotary shaft 4 has a cylindrical shape centered on the axis O1. The rotating shaft 4 is rotatably supported in the housing 1 by a main bearing 9A (bearing device) and a sub-bearing 9B provided at the end on the opposite side in the axial direction from the main bearing 9A. Note that the axial direction is the direction in which the axis O1 extends. The main bearing 9A has a main bearing body 9H that rotatably supports the rotary shaft 4. As shown in FIG. The main bearing body 9H is provided to support the load applied to the rotating shaft 4 from the radial direction. The main bearing 9A has a disc shape centered on the axis O1. The outer peripheral surface of the main bearing 9A is fixed to the inner peripheral surface of the housing 1 by welding, interference fitting, or the like while being in contact with the inner peripheral surface of the housing 1 over the entire circumference. That is, the main bearing 9A divides the space inside the housing 1 into two. A space on one side of the main bearing 9A in the axial direction accommodates the compression portion 2 . The drive unit 3 is accommodated in the space on the opposite side of the main bearing 9A in the axial direction. The suction pipe 11 described above communicates with a space on one side of the main bearing 9A in the axial direction (a space in which the compression portion 2 is accommodated).

The space inside the housing 1 is divided into two spaces by the main bearing 9A. A space on one side in the axial direction of the main bearing 9</b>A in the housing 1 is a suction space V<b>1 that accommodates the compression portion 2 . A space on the other side in the axial direction that includes the main bearing 9A in the housing 1 is a mechanical space V2 that accommodates the drive section 3, the main bearing 9A, and the sub-bearing 9B.

An eccentric shaft 5 is provided at one end of the rotating shaft 4 . The eccentric shaft 5 is provided at a position offset (eccentric) with respect to the axis O1. The eccentric shaft 5 has a columnar shape around an eccentric axis O2 different from the axis O1. The eccentric axis O2 is parallel to the axis O1. The eccentric shaft 5 has a columnar shape protruding from the end of the rotating shaft 4 toward one side in the axial direction (the side where the compression portion 2 is arranged with respect to the main bearing 9A). Therefore, while the rotary shaft 4 is rotating around the axis O1, the eccentric shaft 5 revolves around the axis O1 of the rotary shaft 4. As shown in FIG.

An Oldham ring 91 is provided on the other side of the main bearing 9A in the axial direction. The Oldham ring 91 regulates the rotation (rotation around the eccentric axis O2) of the orbiting scroll 7, which will be described later. Further, a thrust plate 92 is provided on the inner peripheral side of the Oldham ring 91 for supporting the axial load applied to the rotating shaft 4 . The thrust plate 92 has an annular shape centered on the axis O1 when viewed in the axial direction.

A discharge cover 8 is provided on one side of the compressing portion 2 in the axial direction. The discharge cover 8 is a substantially disc-shaped member that partitions the suction space V1 in the axial direction. A discharge chamber 67 is formed in the suction space V1 on one side of the discharge cover 8 in the axial direction. A discharge port 68 is provided in the central portion of the discharge cover 8 to allow the discharge chamber 67 and the compression section 2 to communicate with each other. Further, a flow guide 69 is provided between the discharge cover 8 and the compressing portion 2 to surround the discharge port 68 from the outer peripheral side. The flow guide 69 has a cylindrical shape centered on the axis O1. The high-pressure refrigerant gas flowing out of the compression section 2 is guided by this flow guide 69 and flows into the discharge chamber 67 .

The compression section 2 has a fixed scroll 6 , an orbiting scroll 7 , and a seal portion S provided between the stationary scroll 6 and the orbiting scroll 7 . The fixed scroll 6 is a substantially disc-shaped member fixed to one side of the main bearing 9A in the axial direction inside the housing 1 . The fixed scroll 6 faces the orbiting scroll 7 from the side opposite to the main bearing 9A in the axial direction, thereby forming a compression chamber C therebetween.

More specifically, the fixed scroll 6 has a disk-shaped fixed end plate 61 and a fixed wrap 62 erected from the other surface of the fixed end plate 61 in the axial direction. Fixed end plate 61 extends along a plane perpendicular to axis O1. The fixed wrap 62 is a spirally formed wall when viewed from the axial direction. More specifically, the fixed wrap 62 is formed of a plate-like member wound around the center of the fixed end plate 61 . As an example, the fixed wrap 62 is desirably configured to form an involute curve centered on the axis O1 when viewed from the axial direction.

An outer peripheral wall 63 extending cylindrically along the outer periphery of the fixed end plate 61 is formed on the radially outer side of the fixed wrap 62 . That is, the outer peripheral wall 63 extends axially from the fixed end plate 61 so as to surround the fixed wrap 62 from the radially outer side. Furthermore, an annular flange portion 64 extending radially outward from the inner side is provided on the edge of the outer peripheral wall 63 on the other side in the axial direction (the side on which the driving portion 3 is arranged with respect to the main bearing 9A). is provided. The fixed scroll 6 is fixed to the main bearing 9A via a flange portion 64 with a bolt (not shown) or the like. A fixed scroll discharge port 65 is formed in the central portion of the fixed end plate 61 so as to extend through the fixed end plate 61 in the axial direction. The fixed scroll discharge port 65 is provided with a discharge valve 66 for preventing reverse flow of the refrigerant gas into the compression chamber C. As shown in FIG. The fixed scroll outlet 65 communicates with the discharge port 68 via the flow guide 69 described above. Furthermore, a communication hole 63H is formed in a part of the outer peripheral wall 63 so as to penetrate the outer peripheral wall 63 in the radial direction. The communication hole 63H communicates the inside and the outside of the compression chamber C with each other. The communication hole 63</b>H is formed right beside the opening of the suction pipe 11 so that the position in the axial direction overlaps with the connecting portion between the suction pipe 11 and the housing 1 . Refrigerant gas supplied to the suction space V1 from the suction pipe 11 described above flows into the fixed scroll 6 through the communication hole 63H.

The orbiting scroll 7 has a disk-shaped orbiting end plate 71 and a spiral orbiting wrap 72 provided on the other surface of the orbiting end plate 71 in the axial direction. It is desirable that this turning wrap 72 also form an involute curve centered on the eccentric axis O2.

Further, the orbiting wrap 72 is arranged so as to overlap with the fixed wrap 62 in a direction (radial direction) crossing the axis O1. In other words, the stationary wrap 62 and the swivel wrap 72 mesh with each other. A constant space (compression chamber C) is formed between the stationary wrap 62 and the orbiting wrap 72 in this meshed state. The volume of the compression chamber C changes as the orbiting wrap 72 rotates. This makes it possible to compress the refrigerant gas.

The seal portion S is provided to seal fluid communication (leakage) between the fixed scroll 6 and the orbiting scroll 7 . Here, the fluid includes not only gas such as refrigerant gas compressed in the compression chamber C, but also liquid such as lubricating oil used in the main bearing 9A and the like. As shown in FIG. 2, the seal portion S is provided on the compression portion facing surface 61A of the fixed scroll 6 facing the other side in the axial direction. The compression portion facing surface 61A is an end surface on the other side in the axial direction of the outer peripheral wall 63 and faces the turning end plate 71 side. The compression portion facing surface 61A faces the compression portion sealing surface 71A with a gap G in the axial direction. The compression portion seal surface 71A is an end surface of the turning end plate 71 facing one side in the axial direction (the side opposite to the main bearing 9A side with respect to the turning end plate 71 in the axial direction). The seal portion S suppresses leakage of refrigerant gas from a gap G in the axial direction between the compression portion facing surface 61A and the compression portion sealing surface 71A.

The seal portion S is housed in a housing groove 61R formed on the compression portion facing surface 61A. The housing groove 61R is recessed from the compression portion facing surface 61A toward one side in the axial direction. The accommodation groove 61R of the present embodiment is formed at a position overlapping the outer peripheral wall 63 of the compression portion facing surface 61A when viewed from the axial direction. The housing groove 61R has an annular shape centered on the axis O1 when viewed in the axial direction. That is, the accommodation groove 61R is formed continuously in the circumferential direction with respect to the axis O1.

The seal portion S has a seal portion main body S1 and an elastic portion S2. A portion of the seal body S1 is housed in the housing groove 61R. The seal portion main body S1 is arranged so that a portion thereof protrudes in the axial direction from the compression portion facing surface 61A. As a result, the seal portion main body S1 can come into contact with the compression portion seal surface 71A. The seal body S1 has an annular shape centered on the axis O1 (see FIG. 3). The seal portion main body S1 is integrally formed of, for example, a resin material such as rubber, or a metal material that is relatively resistant to wear. The seal body S1 has an annular shape centered on the axis O1 (see FIG. 3).

The elastic portion S2 biases the seal portion main body S1 toward the compression portion seal surface 71A within the accommodation groove 61R. The elastic portion S2 is made of an elastic material such as silicone rubber. The elastic portion S2 has an annular shape centered on the axis O1, like the seal portion body S1 (see FIG. 3). In the state of being biased by the elastic portion S2, a portion of the seal portion main body S1 protrudes from the accommodation groove 61R toward the other side in the axial direction (the compression portion seal surface 71A side). The material (modulus of elasticity) and the dimension in the axial direction of the elastic portion S2 are determined based on the dimension of the gap G described above. That is, the dimension of the gap G in the axial direction is set in advance, and the material and dimensions of the elastic portion S2 are determined so as to ensure the dimension.

Next, operation of the scroll compressor 100 according to this embodiment will be described. When the operation of the scroll compressor 100 is started, first, the rotating shaft 4 is rotationally driven around the axis O1 by the driving section 3 described above. As the rotary shaft 4 rotates, the eccentric shaft 5 revolves around the axis O1, and the orbiting scroll 7 attached thereto rotates about the axis O1. Here, rotation of the orbiting scroll 7 is restricted by the Oldham ring 91 described above. Therefore, the orbiting scroll 7 makes a circular motion (orbits) about the axis O1 of the rotating shaft 4 along the trajectory drawn by the eccentric axis O2. Along with this orbiting, the orbiting wrap 72 of the orbiting scroll 7 repeats continuous relative movement with respect to the fixed wrap 62 of the fixed scroll 6 . Due to this relative movement, the volume of the compression chamber C formed between the fixed wrap 62 and the orbiting wrap 72 changes over time.

During orbiting of the orbiting scroll 7 , refrigerant gas as a working fluid is introduced into the compression chambers C through the communication holes 63</b>H formed in the outer peripheral wall 63 of the fixed scroll 6 . As the orbiting scroll 7 orbits, the communication hole 63H is closed. As a result, the refrigerant gas is confined within the compression chamber C. As shown in FIG. Subsequently, the orbiting scroll 7 continues to orbit, causing the refrigerant gas to move radially inward (that is, toward the eccentric axis O2 side). At this time, since the orbiting wrap 72 and the stationary wrap 62 have the above-described spiral shape, the volume of the compression chamber C formed by both of them decreases radially inward. This compresses the refrigerant gas. Finally, near the center of the orbiting scroll 7 (or the fixed scroll 6), the refrigerant gas reaches the maximum pressure, and then flows through the fixed scroll discharge port 65, the discharge port 68, and the discharge pipe 12 to the external refrigerant circuit. supplied.

Here, the scroll compressor 100 as described above requires lubricating oil for lubricating the main bearing 9A and the sub-bearing 9B. However, if the refrigerant gas contains lubricating oil, the heat capacity of the refrigerant gas is reduced accordingly. In other words, in order to increase the heat exchange efficiency of the scroll compressor 100, it is necessary to reduce the amount of lubricating oil contained in the refrigerant gas.

Therefore, in the scroll compressor 100 according to the present embodiment, the uncompressed refrigerant gas taken in from the suction pipe 11 is formed in the fixed scroll 6 without passing through the mechanical space V2 (the space where lubricating oil exists). It is directly guided into the compression chamber C through the communication hole 63H. In other words, the refrigerant gas is supplied only to the compression section 2 within the housing 1 without passing around the electric motor 3, the main bearing 9A, and the sub-bearing 9B. As a result, the refrigerant gas is less likely to contain other components such as lubricating oil, and a decrease in the heat capacity of the refrigerant gas can be avoided. As a result, the efficiency of the scroll compressor 100 can be improved while a sufficient amount of lubricating oil is secured to lubricate the main bearing 9A and the sub-bearing 9B.

Furthermore, according to the above configuration, since the fixed scroll 6 is provided with the seal portion S, the fluid flows between the compression portion facing surface 61A of the fixed scroll 6 and the compression portion seal surface 71A of the orbiting scroll 7. (leakage) is sealed. As a result, the possibility that fluid other than the refrigerant gas (for example, lubricating oil) flows into the compression chamber C can be further reduced. That is, it is possible to more positively avoid a decrease in heat capacity caused by mixing other fluids with the refrigerant gas.

In addition, according to the above configuration, the surface of the outer peripheral wall 63 of the fixed scroll 6 facing the orbiting scroll 7 side is the compression portion facing surface 61A. A seal portion S is provided on the compression portion facing surface 61A. This prevents the seal portion S from interfering with other members (for example, other components including the Oldham ring 91 and the thrust plate 92) provided between the turning end plate 71 and the main bearing 9A. . As a result, the seal portion S can be installed without depending on the arrangement of another member, and the diameter of the compression portion 2 can be reduced. As a result, it is possible to further reduce the amount of fluid that flows into the compression chamber C through the space between the compression portion facing surface 61A and the orbiting scroll 7 .

In addition, according to the above configuration, since the seal portion S is accommodated in the accommodation groove 61R, it is possible to prevent the seal portion S from coming off or being displaced during operation of the scroll compressor 100 . Furthermore, since the seal portion S protrudes in the axial direction from the accommodation groove 61R, only the seal portion S can be brought into close contact with the compression portion seal surface 71A. As a result, the circulation of the fluid can be effectively sealed while the orbiting scroll 7 revolves more smoothly.

Furthermore, according to the above configuration, since the seal portion S has an annular shape centered on the axis O1, the compression chamber C can be surrounded from the outer peripheral side with respect to the axis O1 without a gap. As a result, it is possible to further reduce the amount of fluid that flows into the compression chamber C through the space between the compression portion facing surface 61A and the compression portion sealing surface 71A.

In addition, according to the above configuration, since the elastic portion S2 urges the seal portion main body S1 toward the compression portion seal surface 71A, the seal portion main body S1 and the orbiting scroll 7 (compression portion seal surface 71A) can more effectively reduce fluid leakage between Furthermore, even if the seal portion main body S1 is worn out due to use over time, the elastic portion S2 continues to urge the orbiting scroll 7 side, so that the sealing performance can be exhibited for a long period of time.

As described above, the embodiments of the present invention have been described in detail with reference to the drawings. , substitutions, and other modifications are possible. Moreover, the present invention is not limited by the embodiments, but only by the claims.

For example, in the above-described embodiment, an example in which the elastic portion S2 is formed in an annular shape around the axis O1 has been described. However, the mode of the elastic portions S2 is not limited to the above, and they may be arranged at intervals in the circumferential direction along an imaginary circle centered on the axis O1. Furthermore, it is also possible to provide a plurality of seal portions S at intervals in the radial direction with respect to the axis O1. In either configuration, the same effects as those of the above embodiments can be obtained.

Moreover, in the present embodiment, the seal portion S is attached to the compression portion facing surface 61A, but the structure is not limited to this. It is sufficient for the seal portion S to seal between the compression portion facing surface 61A and the compression portion sealing surface 71A. For example, the seal portion S may be attached to the compression portion seal surface 71A. Therefore, the accommodation groove 61R may be formed in the compression portion seal surface 71A.

Further, the sealing portion S may be coated with a highly wear-resistant coating such as DLC on a surface that contacts at least one of the compression portion facing surface 61A and the compression portion sealing surface 71A.

DESCRIPTION OF SYMBOLS 1... Housing 2... Compression part 3... Drive part (electric motor)
4... Rotating shaft (main shaft)
5 Eccentric shaft 6 Fixed scroll 7 Revolving scroll 8 Discharge cover 9A Main bearing (bearing device)
9B Sub-bearing 9H Main bearing body 11 Suction pipe 12 Discharge pipe 61 Fixed end plate 61A Compression portion facing surface 62 Fixed wrap 63 Outer peripheral wall 63H Communication hole 64 Flange 65 Fixed scroll discharge port 66... Discharge valve 67... Discharge chamber 68... Discharge port 71... Orbital end plate 71A... Compressor seal surface 72... Orbital wrap 91... Oldham ring 92... Thrust plate 100... Scroll compressor C... Compression chamber O1... Axis line O2... Eccentricity Axis line S... Seal part S1... Seal part main body S2... Elastic part

Claims (4)

a rotating shaft extending along an axis and rotating about the axis;
a bearing device that rotatably supports the rotating shaft;
a driving unit that rotationally drives the rotating shaft;
a compression section disposed on the opposite side of the driving section in the axial direction in which the axis extends across the bearing device, and compressing a refrigerant by rotating with the rotating shaft;
a housing that accommodates the rotating shaft, the drive section, and the compression section, and stores therein lubricating oil for lubricating the bearing device;
a suction pipe for supplying uncompressed refrigerant into the housing on the compressing portion side in the axial direction with respect to the bearing device,
The outer peripheral surface of the bearing device is fixed in contact with the inner peripheral surface of the housing over the entire circumference,
The compressing section is
an orbiting scroll having a compression portion sealing surface facing the side opposite to the bearing device side in the axial direction, and provided so as to be able to revolve around the axis at a position eccentric to the axis;
a fixed scroll having a compression section facing surface facing the compression section sealing surface in the axial direction and forming a compression chamber for compressing a refrigerant between the orbiting scroll and the orbiting scroll;
a seal portion that is provided between the compression portion seal surface and the compression portion facing surface and seals the flow of fluid;
The fixed scroll is
A disk-shaped end plate centered on the axis;
a spiral fixing wrap provided on one side of the end plate in the axial direction;
an outer peripheral wall surrounding the fixing wrap from the outer peripheral side,
The compression section facing surface is a surface of the outer peripheral wall facing the orbiting scroll,
A communicating hole penetrating in a radial direction is formed in a part of the outer peripheral wall,
The communication hole is formed right beside the opening of the suction pipe so that the position in the axial direction overlaps with the connection portion between the suction pipe and the housing,
The refrigerant flowing from the suction pipe is supplied only to the compression portion through the communication hole without passing around the driving portion and the bearing device in the housing ,
A scroll compressor in which the sealing portion is coated with DLC on a surface in contact with at least one of the compression portion facing surface and the compression portion sealing surface . At least one of the compression portion sealing surface and the compression portion facing surface is formed with an accommodation groove recessed in the axial direction so as to accommodate a portion of the seal portion,
The scroll compressor according to claim 1, wherein the seal portion protrudes in the axial direction from the accommodation groove. The scroll compressor according to claim 1 or 2, wherein the seal portion has an annular shape centered on the axis. The seal portion is
a sealing portion main body abutting against one of the compression portion sealing surface and the compression portion facing surface;
The scroll compressor according to any one of claims 1 to 3, further comprising an elastic portion that biases the seal portion main body toward one of the compression portion sealing surface and the compression portion facing surface.

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