JP7466063B2 - Scroll compressor and refrigeration cycle device - Google Patents

Description

The present invention relates to a scroll compressor, etc.

A known scroll compressor configuration is a so-called double bearing structure in which an orbiting shaft is provided on the orbiting scroll, an orbiting bearing is installed on this orbiting shaft, and a main bearing is installed on a frame radially outside the orbiting bearing. For example, Patent Document 1 describes a scroll compressor with such a double bearing structure in which a main shaft part with an enlarged diameter is provided on the upper part of the shaft, and an orbiting bearing is provided on this main shaft part.

Patent No. 5018832

By using a double bearing structure as in Patent Document 1, the distance between the orbiting scroll and the balance weight is shortened, which not only reduces the weight of the balance weight but also suppresses deflection of the crankshaft due to centrifugal force, especially during high-speed operation.

However, during high-speed operation, the load on the orbiting bearing also increases as the centrifugal force of the orbiting scroll increases. With the technology described in Patent Document 1, it is difficult to suppress this increase in load on the orbiting bearing. It is desirable to suppress overload on the orbiting bearing and further improve the reliability of the scroll compressor, but such technology is not described in Patent Document 1.

Therefore, the objective of the present invention is to provide a highly reliable scroll compressor, etc.

In order to solve the above-mentioned problems, a scroll compressor according to the present invention includes a sealed container, an electric motor having a stator and a rotor and housed in the sealed container, a shaft rotating integrally with the rotor, a fixed scroll having a spiral fixed wrap, an orbiting scroll having a spiral orbiting wrap provided on an end plate and forming a compression chamber between the fixed wrap and the orbiting wrap, an orbiting bearing rotatably supporting the shaft relative to the orbiting scroll, a frame having an insertion hole for the shaft and supporting the fixed scroll, and a main bearing installed in the insertion hole and rotatably supporting an end of the shaft, and a scroll compressor having a rotational movement between the frame and the end plate. and a slewing balance weight which rotates together with the shaft, the shaft and the slewing balance weight are fitted together, a gap is provided between a first fitting portion on the shaft side and a second fitting portion on the slewing balance weight side, an eccentric hole which is eccentric with respect to the central axis of the shaft is provided at the end of the shaft, and as the motor is driven, the slewing bearing comes into contact with the inner circumferential surface of the eccentric hole, a double bearing structure in which the axial installation areas of the main bearing and the slewing bearing partially overlap, and the upper and lower surfaces of the slewing balance weight are plate-shaped and perpendicular to the central axis of the shaft .

The present invention makes it possible to provide highly reliable scroll compressors, etc.

1 is a vertical sectional view of a scroll compressor according to a first embodiment. FIG. 2 is a cross-sectional view of the scroll compressor according to the first embodiment taken along line II-II in FIG. 1. 1 is an exploded perspective view including an orbiting scroll, an orbiting bearing, an orbiting balance weight, and an upper end portion of a crankshaft of a scroll compressor according to a first embodiment. FIG. FIG. 2 is an explanatory diagram illustrating forces acting on each member of the scroll compressor according to the first embodiment, with a region K1 illustrated in FIG. 1 partially enlarged. FIG. 4 is an explanatory diagram showing the relationship between the rotation speed and the load of the scroll compressor according to the first embodiment. 1. FIG. 4 is an enlarged longitudinal sectional view of a portion of a scroll compressor according to a second embodiment, the portion corresponding to a region K1 shown in FIG. FIG. 11 is an exploded perspective view of a scroll compressor according to a second embodiment, including an orbiting scroll, an orbiting bearing, an orbiting balance weight, a partition member, a seal member, and an upper end portion of a crankshaft. FIG. 11 is a perspective view of a partition member of a scroll compressor according to a modified example of the second embodiment. 10 is an enlarged longitudinal sectional view of a portion of a scroll compressor according to a third embodiment, the portion corresponding to a region K1 shown in FIG. FIG. 11 is an exploded perspective view including an orbiting scroll, an orbiting bearing, an orbiting balance weight, a seal member, and an upper end portion of a crankshaft of a scroll compressor according to a third embodiment. FIG. 10 is a configuration diagram of a refrigerant circuit of an air conditioner according to a fourth embodiment.

First Embodiment
<Configuration of Scroll Compressor>
FIG. 1 is a vertical cross-sectional view of a scroll compressor 100 according to the first embodiment.
The scroll compressor 100 shown in Fig. 1 is a device that compresses a gaseous refrigerant. As shown in Fig. 1, the scroll compressor 100 includes a sealed container 1, a compression mechanism 2, a crankshaft 3 (shaft), an electric motor 4, an Oldham ring 5, and balance weights 6a and 6b. In addition to the above-mentioned components, the scroll compressor 100 also includes a fixed member 7, a subframe 8, a lower bearing 9, legs 10, a power supply terminal 11, a main bearing 12, a rotary bearing 13, and a rotary balance weight 14.

The sealed container 1 is a shell-shaped container that houses the compression mechanism 2, crankshaft 3, electric motor 4, etc., and is substantially sealed. Lubricating oil is sealed in the sealed container 1 and is stored as an oil reservoir R1 at the bottom of the sealed container 1. The sealed container 1 comprises a cylindrical tube chamber 1a, a lid chamber 1b that closes the upper side of the tube chamber 1a, and a bottom chamber 1c that closes the lower side of the tube chamber 1a.

As shown in FIG. 1, a suction pipe P1 is inserted and fixed into the lid chamber 1b of the sealed container 1. The suction pipe P1 is a tube that guides refrigerant to the suction port J1 of the compression mechanism 2. A discharge pipe P2 is inserted and fixed into a predetermined location below the frame 21 in the cylindrical chamber 1a of the sealed container 1. The discharge pipe P2 is a tube that guides the refrigerant compressed in the compression mechanism 2 to the outside of the scroll compressor 100.

The compression mechanism 2 is a mechanism that compresses the refrigerant as the crankshaft 3 rotates. The compression mechanism 2 includes a frame 21, a fixed scroll 22, and an orbiting scroll 23, and is disposed in the upper space within the sealed container 1.

The frame 21 is a member that supports the fixed scroll 22, and is fixed inside the sealed container 1. Specifically, the frame 21 is fixed to the cylindrical chamber 1a by welding or the like. The frame 21 is provided with an insertion hole H1 through which the crankshaft 3 (shaft) is inserted.
The fixed scroll 22 is a member that forms a compression chamber S1 together with the orbiting scroll 23 described next. The fixed scroll 22 is installed on the upper side of the frame 21 and fastened to the frame 21 with a bolt B1. As shown in Fig. 1, the fixed scroll 22 includes a base plate 22a and a fixed wrap 22b.

The base plate 22a is a thick member having a circular shape in a plan view. The bottom surface of the base plate 22a is recessed upward at a predetermined position near the center to ensure an area S2 (a circular area in a bottom view) in which the orbiting wrap 23b orbits with respect to the fixed wrap 22b. The base plate 22a is provided with a suction port J1 for introducing the refrigerant through a suction pipe P1.
The fixed wrap 22b has a spiral shape and extends downward from the base plate 22a in the region S2. The lower surface of the base plate 22a (the lower surface of the radially outer portion of the region S2) and the lower end of the fixed wrap 22b are substantially flush with each other.

The orbiting scroll 23 is a member that forms a compression chamber S1 between itself and the fixed scroll 22 by its movement (orbiting), and is provided between the frame 21 and the fixed scroll 22. The orbiting scroll 23 is provided with a disk-shaped mirror plate 23a, a spiral-shaped orbiting wrap 23b erected on the mirror plate 23a, and a rotating shaft 23c extending downward from near the center of the mirror plate 23a. In other words, in the orbiting scroll 23, the orbiting wrap 23b is provided on the upper side (one side) of the mirror plate 23a, and the orbiting shaft 23c is provided on the lower side (the other side) of the mirror plate 23a.

The orbiting wrap 23b is a member that forms the compression chamber S1 together with the fixed wrap 22b. The orbiting shaft 23c is cylindrical and fits into the eccentric hole H2 of the upper end 3b of the crankshaft 3. The spiral fixed wrap 22b and the spiral orbiting wrap 23b mesh with each other to form a compression chamber S1 between the fixed wrap 22b and the orbiting wrap 23b. The compression chamber S1 is a space that compresses the gaseous refrigerant and is formed on the outer line side and inner line side of the orbiting wrap 23b. A discharge port J2 is provided near the center of the base plate 22a of the fixed scroll 22 to guide the refrigerant compressed in the compression chamber S1 to the upper space S3 in the sealed container 1.

The crankshaft 3 (shaft) is an axis that rotates integrally with the rotor 4b of the electric motor 4, and extends in the vertical direction. As shown in Fig. 1, the crankshaft 3 has a main shaft portion 3a, an upper end portion 3b, a lower shaft portion 3c, and an oil supply piece 3d. The upper end portion 3b of the crankshaft 3 is journaled by the main bearing 12, and the lower shaft portion 3c is journaled by the lower bearing 9.

The main shaft portion 3a is fixed coaxially to the rotor 4b of the electric motor 4 and rotates integrally with the rotor 4b. The upper end portion 3b extends upward from the main shaft portion 3a and has a bottomed cylindrical shape that opens upward. The upper end portion 3b (end portion) of the crankshaft 3 (shaft) is provided with an eccentric hole H2 that is eccentric with respect to the central axis Z1 of the crankshaft 3. In other words, the central axis (not shown) of the eccentric hole H2, which has a circular shape in cross section, is eccentric with respect to the central axis Z1 of the crankshaft 3 (main shaft portion 3a, etc.).

The swivel shaft 23c with the swivel bearing 13 installed is fitted into the eccentric hole H2. A minute radial gap is provided between the inner peripheral surface of the eccentric hole H2 and the swivel bearing 13 to allow lubricating oil to enter. When the electric motor 4 is driven, the swivel shaft 23c rotates eccentrically relative to the main shaft portion 3a.

At the upper end 3b (end) of the crankshaft 3 (shaft), a protrusion 31b (see also FIG. 2) that protrudes upward (toward the orbiting scroll 23) is provided as a "first fitting portion." As will be described in detail later, the protrusion 31b is fitted into a fitting hole H3 (no reference number is shown in FIG. 1, see FIG. 2) of the orbiting balance weight 14.

The lower shaft portion 3c of the crankshaft 3 is supported by the lower bearing 9 and extends below the main shaft portion 3a. The oil supply piece 3d is a portion that draws up lubricating oil from the oil reservoir R1 of the sealed container 1 and extends downward from the lower shaft portion 3c in an elongated manner. A positive displacement pump, centrifugal pump, etc. may be provided in the oil supply piece 3d.

As shown in Figure 1, the crankshaft 3 (i.e., the main shaft portion 3a, the upper end portion 3b, the lower shaft portion 3c, and the oil supply piece 3d) is provided with an oil supply passage 3e that guides lubricating oil. The lubricating oil stored in the sealed container 1 as an oil reservoir R1 rises through the oil supply passage 3e and is guided to the eccentric hole H2 in the upper end portion 3b. The oil supply passage 3e also branches out in a predetermined manner so that lubricating oil is also supplied to the lower bearing 9, main bearing 12, slewing bearing 13, etc.

The electric motor 4 is a drive source that rotates the crankshaft 3, and is provided between the frame 21 and the subframe 8 in the axial direction. As shown in FIG. 1, the electric motor 4 includes a stator 4a and a rotor 4b. The stator 4a has a winding 41a and is fixed to the inner peripheral surface of the cylindrical chamber 1a. The rotor 4b is arranged rotatably radially inside the stator 4a. The crankshaft 3 is fixed to the rotor 4b by press-fitting or the like so that it is coaxial with the central axis Z1.

The Oldham ring 5 is a ring-shaped member that receives the eccentric rotation of the orbiting shaft 23c and causes the orbiting scroll 23 to revolve (orbit) without rotating on its axis. As shown in Fig. 1, the Oldham ring 5 is provided between the frame 21 and the orbiting scroll 23. Specifically, the Oldham ring 5 is installed in a groove (not shown) formed in the lower surface of the orbiting scroll 23, and is also installed in a groove (not shown) formed in the frame 21.
The balance weights 6a and 6b are members for suppressing vibration of the scroll compressor 100. In the example of Fig. 1, the balance weight 6a is provided on the upper side of the rotor 4b in the main shaft portion 3a, and another balance weight 6b is provided on the lower surface of the rotor 4b.

The fixing member 7 is a member that fixes the position of the subframe 8, and is fixed to the inner surface of the sealed container 1 by welding or the like. The subframe 8 is a member on which the lower bearing 9 is installed, and is fastened to the fixing member 7 with bolts B2. The subframe 8 is provided with a hole (number not shown) through which the crankshaft 3 is inserted. The lower bearing 9 supports the lower shaft portion 3c of the crankshaft 3 so that it can rotate freely, and is installed on the inner surface of the hole in the subframe 8.

The legs 10 are members that support the sealed container 1 and are installed in the bottom chamber 1c. The power supply terminal 11 is a terminal used to supply power to the electric motor 4. This power supply terminal 11 is installed in the cylindrical chamber 1a and is electrically connected to the winding 41a of the electric motor 4.

The main bearing 12 rotatably supports the upper end 3b of the crankshaft 3 with respect to the frame 21, and is fixed by press fitting or the like into an insertion hole H1 of the frame 21. As such a main bearing 12, for example, a cylindrical sliding bearing is used.
The orbiting bearing 13 rotatably supports an upper end portion 3b of the crankshaft 3 (shaft) relative to the orbiting scroll 23, and is fixed to an outer peripheral surface of the orbiting shaft 23c by press-fitting or the like. As such an orbiting bearing 13, for example, a cylindrical plain bearing is used.

As shown in FIG. 1, the main bearing 12 and the swivel bearing 13 are installed in areas that partially overlap in the axial direction. This double bearing structure can shorten the axial distance between the point of application of force from the main bearing 12 to the crankshaft 3 and the point of application of force from the swivel bearing 13 to the crankshaft 3. This can suppress the generation of a moment that tilts the crankshaft 3, and thus suppress the bending and uneven contact of the crankshaft 3. In addition, the double bearing structure can shorten the length of the crankshaft 3, which can reduce the size and cost of the scroll compressor 100.

1 is a member for reducing the load acting on the orbiting bearing 13, and is provided between the frame 21 and the end plate 23a. In other words, the orbiting balance weight 14 is installed so as to fit in the space between the frame 21 and the orbiting scroll 23. From another perspective, the positional relationship of the orbiting balance weight 14 can also be said to be provided between the crankshaft 3 and the end plate 23a.

As described above, the swivel shaft 23c with the swivel bearing 13 installed is fitted into the eccentric hole H2, but the upper end of the swivel bearing 13 is exposed from the eccentric hole H2. The swivel balance weight 14 is provided radially outward from the portion where the swivel bearing 13 is exposed from the eccentric hole H2 (the upper end of the swivel bearing 13). The configuration including such a swivel balance weight 14 will be described in detail with reference to FIG. 2.

FIG. 2 is a cross-sectional view of the scroll compressor taken along line II-II in FIG.
In addition, the sealed container 1 (see FIG. 1), the Oldham ring 5 (see FIG. 1), the frame 21 (see FIG. 1), etc. are omitted in Fig. 2. Fig. 2 also illustrates the central axis Z1 of the crankshaft 3, the central axis Z2 of the revolving shaft 23c, and the center of gravity G1 of the revolving balance weight 14.

2, a hole H4 having a circular shape in cross section is provided in the swivel balance weight 14 with respect to the central axis Z2 of the swivel shaft 23c. The diameter of the hole H4 in the swivel balance weight 14 is slightly larger than the outer diameter of the swivel bearing 13. In other words, a minute gap (not shown) is provided in the radial direction between the inner peripheral surface of the hole H4 in the swivel balance weight 14 and the outer peripheral surface of the swivel bearing 13. By providing such a minute gap, the swivel balance weight 14 is movable in the circumferential direction relative to the swivel shaft 23c and the swivel bearing 13. In other words, the swivel balance weight 14 is rotatably supported by the swivel bearing 13.

The orbiting balance weight 14 has a semicircular weight portion 14a in cross section in the area opposite to the "eccentric side" of the orbiting shaft 23c. The "eccentric side" of the orbiting shaft 23c (i.e., the eccentric side of the eccentric hole H2 in FIG. 1) is the side where the central axis Z2 of the orbiting shaft 23c is eccentric with respect to the central axis Z1 of the crankshaft 3 (the right side of the paper in FIG. 2). In other words, the center of gravity G1 of the orbiting balance weight 14 is located on the opposite side of the central axis Z2 of the orbiting shaft 23c with respect to the central axis Z1 of the crankshaft 3. As a result, part of the centrifugal force of the orbiting scroll 23 is offset by the orbiting balance weight 14, so that the load on the orbiting bearing 13 can be reduced.

The crankshaft 3 (shaft) and the swing balance weight 14 are fitted together. That is, the weight portion 14a of the swing balance weight 14 is provided with a fitting hole H3, which is a hole that fits into the protrusion 31b (first fitting portion: see also FIG. 1) of the crankshaft 3, as a "second fitting portion". A gap is provided between the protrusion 31b, which is the "first fitting portion" on the crankshaft 3 (shaft), and the fitting hole H3, which is the "second fitting portion" on the swing balance weight 14. To explain in more detail, as shown in FIG. 2, radial gaps C1 and C2 are provided between the inner wall surface of the fitting hole H3 and the protrusion 31b, with the central axis Z1 of the crankshaft 3 as the reference (center). The gap C1 on the radial outside of the protrusion 31b and the gap C2 on the radial inside of the protrusion 31b are each formed to be sufficiently larger than the tiny gap (symbol not shown) between the peripheral wall surface of the hole H4 of the slewing balance weight 14 and the slewing bearing 13.

In other words, the radial length of each of the gaps C1, C2 between the inner wall surface of the fitting hole H3 (second fitting portion) and the protrusion 31b is longer than the radial length of the gap between the swing bearing 13 and the swing balance weight 14. As a result, when a force (gas load or centrifugal force) acts to move the swing balance weight 14 in the radial direction, the swing bearing 13 comes into contact with the peripheral wall surface of the hole H4, and further movement is restricted. In this way, the swing balance weight 14 is configured to directly apply a radial force to the swing bearing 13.
Incidentally, a small gap is also provided between the inner wall surface of the fitting hole H3 and the protrusion 31b in the circumferential direction based on (centered on) the central axis Z1 of the crankshaft 3. In other words, a predetermined gap is provided between the inner wall surface of the fitting hole H3 and the protrusion 31b in a direction perpendicular to the central axis Z1 of the crankshaft 3 (a horizontal direction including the radial and circumferential directions).

FIG. 3 is an exploded perspective view including the orbiting scroll 23, the orbiting bearing 13, the orbiting balance weight 14, and the upper end portion 3b of the crankshaft 3. As shown in FIG.
In FIG. 3, the orbiting scroll 23 and the orbiting bearing 13 are shown cut along a predetermined plane (not shown) including the central axis Z1 of the crankshaft 3 (see FIG. 1).
As described above, the upper end 3b of the crankshaft 3 is provided with the projection 31b that projects upward. On the other hand, the swing balance weight 14 is provided with a fitting hole H3 into which the projection 31b is fitted.

When the crankshaft 3 rotates as the electric motor 4 (see FIG. 1) is driven, the protrusion 31b moves in the circumferential direction, and a force is exerted on the inner wall surface of the fitting hole H3 in the circumferential direction (the tangential direction when the protrusion 31b rotates) (see also FIG. 2). As a result, the swing balance weight 14 rotates together with the crankshaft 3. In other words, the swing balance weight 14 rotates synchronously with the crankshaft 3 (rotating so that the rotation angle is equal).

When the crankshaft 3 rotates due to the drive of the electric motor 4 shown in FIG. 1, the rotating shaft 23c fitted in the eccentric hole H2 of the upper end 3b rotates accordingly. As a result, the compression chamber S1 between the fixed scroll 22 and the rotating scroll 23 shrinks, and the refrigerant is compressed. The compressed refrigerant is discharged into the upper space S3 in the sealed container 1 through the discharge port J2 of the fixed scroll 22. The refrigerant discharged into the upper space S3 in this manner is guided to the space below the compression mechanism 2 through a flow path (not shown) between the sealed container 1 and the compression mechanism 2, and is further discharged to the outside of the sealed container 1 through the discharge pipe P2.

<Action>
FIG. 4 is an explanatory diagram showing forces acting on each member by partially enlarging an area K1 shown in FIG.
When the orbiting scroll 23 orbits, as the center of gravity of the orbiting scroll 23 moves, a centrifugal force Fcos shown by the white arrows in Fig. 4 acts on the orbiting scroll 23. In addition, as a reaction to the compression of the refrigerant, a gas load (white arrows are not shown) is generated in the tangential direction and radial direction of the movement of the orbiting scroll 23.

Here, the centrifugal force Fcos acting on the orbiting scroll 23 increases in proportion to the square of the moving speed of the orbiting scroll 23, so the increase in the centrifugal force Fcos of the orbiting scroll 23 becomes noticeable, especially in the high-speed range. Therefore, in a conventional configuration in which the orbiting balance weight 14 is not provided, if the upper limit speed of the scroll compressor is increased, there is a possibility that the orbiting bearing 13 will be overloaded. In addition, in the conventional configuration, the oil film thickness on the outer periphery of the orbiting bearing 13 becomes thin, especially in the high-speed range, and the friction coefficient due to direct contact between the inner periphery of the eccentric hole H2 and the orbiting bearing 13 increases, which may cause wear or seizure of the orbiting bearing 13, etc.

In contrast, in the first embodiment, the orbiting balance weight 14 is provided between the end plate 23a of the orbiting scroll 23 and the frame 21. As described above, the orbiting balance weight 14 is eccentric to the opposite side of the orbiting axis 23c of the orbiting scroll 23 (see FIG. 2). Therefore, the centrifugal force Fcob acting on the orbiting balance weight 14 acts in the opposite direction to the centrifugal force Fcos of the orbiting scroll 23. As a result, a load Fr of a magnitude obtained by subtracting the centrifugal force Fcob of the orbiting balance weight 14 from the centrifugal force Fcos of the orbiting scroll 23 acts on the orbiting bearing 13 as a reaction force to the centrifugal force.

FIG. 5 is an explanatory diagram showing the relationship between the rotation speed and the load of the scroll compressor (also see FIG. 4 as appropriate).
In addition, the horizontal axis of Fig. 5 is the rotation speed of the scroll compressor 100 (i.e., the rotation speed of the electric motor 4), and the vertical axis is the load. The dashed line in Fig. 5 is the horizontal gas load Fg caused by the compression of the refrigerant. The dashed line in Fig. 5 is the centrifugal force Fcos acting on the orbiting scroll 23. The white arrow in Fig. 5 is the centrifugal force Fcob acting on the orbiting balance weight 14. The solid line in Fig. 5 is the load Fr acting on the orbiting bearing 13 as a reaction force to the centrifugal force.

As shown in Figure 5, the gas load Fg caused by the compression of the refrigerant is approximately constant regardless of the rotation speed of the scroll compressor 100. On the other hand, the centrifugal force Fcos of the orbiting scroll 23 increases in proportion to the square of the rotation speed of the scroll compressor 100. If the orbiting balance weight 14 were not provided, the sum of the gas load Fg and the centrifugal force Fcos would act on the orbiting bearing 13, which could result in an overload on the orbiting bearing 13 at high speeds.

In contrast, in the first embodiment, since the orbiting balance weight 14 is provided, the load Fr acting on the orbiting bearing 13 as a reaction force to the centrifugal force is the centrifugal force Fcos of the orbiting scroll 23 minus the centrifugal force Fcob of the orbiting balance weight 14 (Fr = Fcos - Fcob). The sum of this load Fr and the gas load Fg acts on the orbiting bearing 13. Therefore, the load on the orbiting bearing 13 can be significantly reduced, especially in the high-speed range where the centrifugal force of the orbiting scroll 23 increases. The space between the orbiting scroll 23 and the frame 21 is filled with lubricating oil after lubricating the main bearing 12 and the orbiting bearing 13. In other words, an oil film is formed between the inner circumferential surface of the hole H4 (see FIG. 2) of the orbiting balance weight 14 and the orbiting bearing 13, so that a good lubricated state is maintained.

＜Effects＞
According to the first embodiment, a gap (gaps C1, C2, etc. in FIG. 2) is provided between the protrusion 31b (first fitting portion: see FIG. 2) of the crankshaft 3 and the fitting hole H3 (second fitting portion: see FIG. 2) of the orbiting balance weight 14. Therefore, when the protrusion 31b presses the wall surface of the fitting hole H3 in the circumferential direction to rotate the orbiting balance weight 14, the orbiting balance weight 14 moves radially by centrifugal force within the range of the gap and contacts the orbiting bearing 13. As a result, in this orbiting bearing 13, a part of the centrifugal force Fcos (see FIG. 4) of the orbiting scroll 23 is canceled by the centrifugal force Fcob (see FIG. 4) of the orbiting balance weight 14. This allows the load on the orbiting bearing 13 to be significantly reduced, especially in the high-speed range where the centrifugal force of the orbiting scroll 23 increases. In addition, since the oil film thickness of the lubricating oil in the slewing bearing 13 is sufficiently ensured, the friction loss of the slewing bearing 13 can be reduced and wear and seizure of the slewing bearing 13 can be suppressed.

It is also possible to increase the upper limit of the rotational speed of the scroll compressor 100 (to achieve even higher speeds) while ensuring the reliability of the orbiting bearing 13. In this way, according to the first embodiment, a scroll compressor 100 with high performance and reliability can be provided. In addition, an orbiting balance weight 14 is provided between the orbiting scroll 23 and the frame 21, so that the centrifugal force of the orbiting balance weight 14 acts directly on the orbiting bearing 13. This not only reduces the load on the orbiting bearing 13, but also suppresses deflection of the crankshaft 3.

Second Embodiment
The second embodiment differs from the first embodiment in that a partition member 15 (see FIG. 6) is provided between the orbiting scroll 23 and the frame 21, but is otherwise similar to the first embodiment (such as the overall configuration of the scroll compressor: see FIG. 1). Therefore, only the parts that differ from the first embodiment will be described, and a description of the overlapping parts will be omitted.

FIG. 6 is an enlarged vertical cross-sectional view of a portion of a scroll compressor 100A according to the second embodiment, which corresponds to the region K1 shown in FIG.
As shown in FIG. 6, the scroll compressor 100A includes a partition member 15 and two seal members 16a and 16b in addition to the components described in the first embodiment.
The partition member 15 is a member that divides the space between the orbiting scroll 23 and the frame 21 into a discharge pressure space S4 (first region) including the insertion hole H1 of the crankshaft 3 and a back pressure chamber S5 (second region) radially outward of the discharge pressure space S4, as viewed from the direction of the central axis Z1 of the crankshaft 3. As shown in Fig. 6, the partition member 15 is provided between the orbiting scroll 23 and the frame 21. In addition, an orbiting balance weight 14 is provided inside the partition member 15.

Lubricating oil flows into the discharge pressure space S4 inside the partition member 15 after lubricating the main bearing 12, the swivel bearing 13, etc. This lubricating oil has a pressure approximately equal to the discharge pressure of the refrigerant compressed by the compression mechanism 2. Therefore, the pressure in the discharge pressure space S4 is approximately equal to the discharge pressure described above. In addition, if the pressure in the back pressure chamber S5 becomes lower than that in the discharge pressure space S4, the pressure difference is maintained because the discharge pressure space S4 and the back pressure chamber S5 are separated by the partition member 15.

The pressure in the back pressure chamber S5 (back pressure) can be adjusted, for example, by intermittently connecting the compression chamber S1 and the back pressure chamber S5 in accordance with the movement of the orbiting scroll 23, or by providing a back pressure valve (not shown). By providing such a back pressure chamber S5, it is possible to prevent the force pressing the orbiting scroll 23 upward against the fixed scroll 22 from becoming too large.

FIG. 7 is an exploded perspective view including the orbiting scroll 23, the orbiting bearing 13, the orbiting balance weight 14, the partition member 15, the seal member 16a, and the upper end portion 3b of the crankshaft 3 of the scroll compressor 100A.
7, the orbiting scroll 23, the orbiting bearing 13, the partition member 15, and the seal member 16a are shown cut along a predetermined plane (not shown) including the central axis Z1 (see FIG. 6) of the crankshaft 3. Also, in FIG. 7, the seal member 16b (see FIG. 6) on the inner side of the partition member 15 is not shown.

As shown in Fig. 7, the partition member 15 includes an annular portion 15a and a peripheral wall 15b. The annular portion 15a is annular when viewed from the direction of the central axis Z1 (see Fig. 1) of the crankshaft 3 (shaft), and surrounds the slewing bearing 13 (see also Fig. 6). The peripheral wall 15b extends downward (towards the frame 21: see Fig. 6) from the outer periphery of the annular portion 15a. As shown in Fig. 6, the edge portion 151b (lower end) of the peripheral wall 15b of the partition member 15 abuts against the frame 21. Such a partition member 15 may be made of, for example, metal or resin.

The sealing member 16a shown in Figure 6 is a resin member that seals the small gap between the annular portion 15a of the partition member 15 and the end plate 23a of the orbiting scroll 23. In the example of Figure 6, an annular groove M1 is formed on the underside of the end plate 23a, and the sealing member 16a is installed in this groove M1. The sealing member 16a is compressed in the vertical direction by the partition member 15 and the end plate 23a.

As shown in Fig. 6, the frame 21 has a thick-walled portion 21a that is annular in plan view in a portion including the peripheral wall surface of the insertion hole H1. The thick-walled portion 21a is formed to be thicker in the axial direction than on its outer periphery and protrudes upward (toward the orbiting scroll 23).

The sealing member 16b shown in Figure 6 is a resin member that seals the small gap between the peripheral wall 15b of the partition member 15 and the thick portion 21a of the frame 21. In the example of Figure 6, an annular groove M2 is formed on the outer peripheral surface of the thick portion 21a of the frame 21, and the sealing member 16b is installed in this groove M2. The sealing member 16b is compressed in the radial direction by the partition member 15 and the frame 21. By providing these sealing members 16a, 16b, leakage of refrigerant from the inside to the outside of the partition member 15 can be suppressed.

＜Effects＞
According to the second embodiment, the partition member 15 (see FIG. 6) divides the space between the orbiting scroll 23 and the frame 21 into a discharge pressure space S4 and a back pressure chamber S5. This makes it possible to prevent the crankshaft 3 from floating up due to the pressure difference between the top and bottom, even in a structure in which the discharge pressure acts on the lower end of the crankshaft 3. In addition, by adjusting the pressure (back pressure) in the back pressure chamber S5, it is possible to reduce the thrust load (axial load) when the orbiting scroll 23 is pressed against the fixed scroll 22. As a result, it is possible to reduce friction loss in the compression mechanism 2 and suppress wear and seizure.

<Modification of the second embodiment>
In the second embodiment, a configuration in which no groove is provided in the partition member 15 (see FIG. 7) has been described, but the present invention is not limited to this. For example, as will be described next, a radial groove 15c may be provided in the upper surface of the annular portion 15a of the partition member 15A (see FIG. 8) so that the lubricating oil flows through this groove 15c.

FIG. 8 is a perspective view of a partition member 15A of a scroll compressor according to a modified example of the second embodiment.
In the modification shown in Fig. 8, a groove 15c is provided on the upper surface of the annular portion 15a of the partition member 15A. To explain in more detail, the groove 15c is provided in the radial direction from the inner peripheral edge to the outer peripheral edge of the annular portion 15a. This groove 15c is a flow path that guides the lubricating oil that has lubricated the main bearing 12, the orbiting bearing 13, etc. from the discharge pressure space S4 (see Fig. 6) to the back pressure chamber S5 (see Fig. 6).

By providing minute grooves 15c on the upper surface of partition member 15A in this way, the lubricating oil flowing in from discharge pressure space S4 (see FIG. 6) is throttled by groove 15c and then directed to back pressure chamber S5 (see FIG. 6). This allows the pressure (back pressure) in back pressure chamber S5 to be adjusted, for example, by appropriately adjusting the flow path cross-sectional area of groove 15c at the design stage. Note that while FIG. 8 shows an example in which one groove 15c is provided, multiple grooves may be provided.

In addition, instead of the groove 15c shown in Figure 8, a groove (not shown) serving as a flow path for guiding lubricating oil from the discharge pressure space S4 (see Figure 6) to the back pressure chamber S5 (see Figure 6) may be provided on the underside of the end plate 23a (see Figure 6) of the orbiting scroll 23.
Also, a groove 15c (see FIG. 8) may be provided on the upper surface of the partition member 15A, and a groove (not shown) may be provided on the lower surface of the end plate 23a (see FIG. 6) of the orbiting scroll 23. Here, the groove (not shown) provided on the lower surface of the end plate 23a and the groove 15c provided on the upper surface of the partition member 15A may or may not overlap in a plan view.

In this way, a groove (such as groove 15c in FIG. 8) that guides lubricating oil from the discharge pressure space S4 (first region) to the back pressure chamber S5 (second region) is provided on the surface of the partition member 15A facing the orbiting scroll 23 and/or the surface of the end plate 23a facing the partition member 15A. With this configuration, the pressure in the back pressure chamber S5 (see FIG. 6) can be adjusted by appropriately adjusting the flow path cross-sectional area of the groove 15c etc. at the design stage.

Third Embodiment
The third embodiment differs from the second embodiment in that two seal members 17a, 17b (see FIG. 9) are provided instead of the partition member 15A (see FIG. 6), but other points (such as the overall configuration of the scroll compressor) are similar to those of the second embodiment. Therefore, only the parts that differ from the second embodiment will be described, and a description of the overlapping parts will be omitted.

FIG. 9 is an enlarged vertical cross-sectional view of a portion of a scroll compressor 100B according to the third embodiment, which corresponds to the region K1 shown in FIG.
9, the scroll compressor 100B includes two seal members 17a, 17b that are installed on the orbiting balance weight 14B. These seal members 17a, 17b are resin members that partition the space between the orbiting scroll 23 and the frame 21 in the radial direction into a discharge pressure space S4 (first region) that includes the insertion hole H1 of the crankshaft 3 (shaft) and a back pressure chamber S5 (second region) that is located radially outside the discharge pressure space S4.

FIG. 10 is an exploded perspective view including the orbiting scroll 23, the orbiting bearing 13, the orbiting balance weight 14B, the seal members 17a and 17b, and the upper end portion 3b of the crankshaft 3 of the scroll compressor 100B.
As shown in Fig. 10, an annular groove M3 (see also Fig. 9) is formed on the top surface of the swing balance weight 14B. An annular seal member 17a (first seal member) is installed in this groove M3. As shown in Fig. 9, the annular seal member 17a is provided in the gap between the swing balance weight 14B and the end plate 23a.

Meanwhile, an annular groove M4 (see FIG. 9) is also formed on the underside of the swing balance weight 14B. An annular seal member 17b (second seal member) is installed in this groove M4. As shown in FIG. 9, the annular seal member 17b is provided in the gap between the swing balance weight 14B and the frame 21. In order to provide the annular grooves M3 and M4, the diameter of the annular portion 14b including the peripheral wall surface of the hole H4 of the swing balance weight 14B is longer than in the first embodiment (see FIG. 3).

During operation of the scroll compressor 100B, the orbiting balance weight 14B and the seal members 17a and 17b move (rotate) together in the circumferential direction. That is, one of the seal members 17a moves in the circumferential direction together with the orbiting balance weight 14B while being compressed in the vertical direction between the orbiting balance weight 14B and the orbiting scroll 23. The other seal member 17b moves in the circumferential direction together with the orbiting balance weight 14B while being compressed in the vertical direction between the orbiting balance weight 14B and the frame 21.

＜Effects＞
According to the third embodiment, by providing two seal members 17a and 17b, the space between the orbiting scroll 23 and the frame 21 can be divided into a discharge pressure space S4 (see FIG. 9) and a back pressure chamber S5 (see FIG. 9). Also, unlike the second embodiment, the radial size of the orbiting balance weight 14B is not particularly limited to a size that can be accommodated in the partition member 15 (see FIG. 6). Therefore, according to the third embodiment, the outer diameter of the orbiting balance weight 14B can be sufficiently secured. This further reduces the load on the orbiting bearing 13, and thus improves the performance and reliability of the scroll compressor 100B.

<Modification of the third embodiment>
In the third embodiment, the case where two seal members 17a, 17b are provided on the orbiting balance weight 14B has been described, but this is not limiting. For example, an annular groove (not shown) may be provided on the lower surface of the end plate 23a of the orbiting scroll 23, and the seal member 17a (first seal member) may be provided in this groove. Also, an annular groove (not shown) may be provided on the upper surface of the frame 21, and the seal member 17b (second seal member) may be provided in this groove. With such a configuration, the same effects as those of the third embodiment can be achieved.

In addition, a groove (not shown) for guiding lubricating oil from the discharge pressure space S4 to the back pressure chamber S5 may be provided on at least one of the lower surface (surface on the orbiting balance weight 14 side) of the mirror plate 23a of the orbiting scroll 23 and the upper surface (surface on the orbiting balance weight 14 side) of the frame 21. This allows the pressure (back pressure) of the back pressure chamber S5 to be adjusted by appropriately adjusting the flow path cross-sectional area of the groove (not shown) at the design stage.

Fourth Embodiment
In the fourth embodiment, an air conditioner W1 (refrigeration cycle device: see FIG. 11) including the scroll compressor 100 (see FIG. 1) described in the first embodiment will be described.

FIG. 11 is a configuration diagram of a refrigerant circuit Q1 of an air conditioner W1 according to the fourth embodiment.
In addition, the solid arrows in FIG. 11 indicate the flow of the refrigerant during heating operation.
On the other hand, the dashed arrows in FIG. 11 indicate the flow of the refrigerant during cooling operation.
The air conditioner W1 is a device that performs air conditioning such as cooling and heating. As shown in Fig. 11, the air conditioner W1 includes a scroll compressor 100, an outdoor heat exchanger 71, an outdoor fan 72, an expansion valve 73, a four-way valve 74, an indoor heat exchanger 75, and an indoor fan 76.

In the example of FIG. 11, the scroll compressor 100, the outdoor heat exchanger 71, the outdoor fan 72, the expansion valve 73, and the four-way valve 74 are provided in the outdoor unit 81. On the other hand, the indoor heat exchanger 75 and the indoor fan 76 are provided in the indoor unit 82.

The scroll compressor 100 is a device that compresses a gaseous refrigerant, and has a configuration similar to that of the first embodiment (see FIG. 1). The outdoor heat exchanger 71 is a heat exchanger in which heat exchange takes place between the refrigerant flowing through its heat transfer tube (not shown) and the outside air sent in from the outdoor fan 72. The outdoor fan 72 is a fan that sends outside air to the outdoor heat exchanger 71. The outdoor fan 72 is equipped with an outdoor fan motor 72a as a drive source, and is installed near the outdoor heat exchanger 71.

The indoor heat exchanger 75 is a heat exchanger in which heat is exchanged between the refrigerant flowing through its heat transfer tube (not shown) and the indoor air (air in the air-conditioned room) sent from the indoor fan 76. The indoor fan 76 is a fan that sends indoor air to the indoor heat exchanger 75. This indoor fan 76 is equipped with an indoor fan motor 76a as a driving source, and is installed near the indoor heat exchanger 75.

The expansion valve 73 is a valve that reduces the pressure of the refrigerant condensed in the "condenser" (one of the outdoor heat exchanger 71 and the indoor heat exchanger 75). The refrigerant reduced in pressure by the expansion valve 73 is led to the "evaporator" (the other of the outdoor heat exchanger 71 and the indoor heat exchanger 75).

The four-way valve 74 is a valve that switches the flow path of the refrigerant depending on the operation mode of the air conditioner W1. For example, during cooling operation (see the dashed arrow in FIG. 11), the refrigerant circulates in the refrigerant circuit Q1 through the scroll compressor 100, the outdoor heat exchanger 71 (condenser), the expansion valve 73, and the indoor heat exchanger 75 (evaporator) in sequence. On the other hand, during heating operation (see the solid arrow in FIG. 11), the refrigerant circulates in the refrigerant circuit Q1 through the scroll compressor 100, the indoor heat exchanger 75 (condenser), the expansion valve 73, and the outdoor heat exchanger 71 (evaporator) in sequence. In addition to the scroll compressor 100 and the outdoor fan 72, the expansion valve 73, the four-way valve 74, the indoor fan 76, and other devices are controlled in a predetermined manner by a control device (not shown).

＜Effects＞
According to the fourth embodiment, the air conditioner W1 includes a scroll compressor 100 having a similar configuration to that of the first embodiment. This makes it possible to improve the performance and reliability of the air conditioner W1 as a whole.

<<Variations>>
Although the scroll compressor 100 and the air conditioner W1 according to the present invention have been described in each embodiment above, the present invention is not limited to these descriptions and various modifications can be made.
For example, in each embodiment, the scroll compressor 100 having a double bearing structure (see FIG. 1) has been described, but the present invention is not limited thereto. That is, in the orbiting scroll 23, the orbiting wrap 23b may be provided on the upper side (one side in the axial direction) of the end plate 23a, while a boss portion (not shown) may be provided on the lower side (the other side in the axial direction) of the end plate 23a, and the eccentric portion (not shown) of the crankshaft 3 may be fitted into the recess of the boss portion. In such a configuration, the orbiting balance weight 14 is provided between the frame 21 and the end plate 23a, and rotates together with the crankshaft 3. Note that the crankshaft 3 (shaft) and the orbiting balance weight 14 are fitted together, and a predetermined gap (for example, a gap in a direction perpendicular to the central axis of the crankshaft 3) is provided between the "first fitting portion" on the crankshaft 3 side and the "second fitting portion" on the orbiting balance weight 14 side. The center of gravity of the orbiting balance weight 14 is located on the side opposite to the side where the eccentric portion (not shown) of the crankshaft 3 is eccentric with respect to the central axis Z1. Even with this configuration, the load acting on the orbiting bearing 13 as a reaction force to the centrifugal force can be reduced, thereby improving the performance and reliability of the scroll compressor. The second embodiment can also be applied to this configuration, and the third and fourth embodiments can also be applied.

In addition, in each embodiment, a fitting hole H3 (second fitting portion) is provided in the swing balance weight 14 (see FIG. 2), and the protrusion 31b (first fitting portion) of the crankshaft 3 is fitted into the fitting hole H3, but this is not limited to the configuration. For example, a fitting groove (second fitting portion: not shown) may be provided as a groove that fits into the swing balance weight 14, and the protrusion 31b (first fitting portion) of the crankshaft 3 may be fitted into this fitting groove. In other words, a "second fitting portion" that is a hole or groove that fits into the protrusion 31b may be provided in the swing balance weight 14.

Also, a protrusion (second fitting portion: not shown) extending axially downward (toward the frame 21) may be provided on the swing balance weight 14, while a fitting hole or fitting groove (first fitting portion: not shown) into which the protrusion is fitted may be provided on the upper end portion 3b of the crankshaft 3. In such a configuration, a gap (for example, a gap in a direction perpendicular to the central axis of the crankshaft 3) may be provided between the "first fitting portion" on the crankshaft 3 side and the "second fitting portion" on the swing balance weight 14 side. With such a configuration, the same effects as those of the respective embodiments can be achieved.
In addition, in each embodiment, the main bearing 12 (see FIG. 1) and the frame 21 (see FIG. 1) are separate bodies, but this is not limited thereto. For example, the peripheral wall surface of the insertion hole H1 in the frame 21 may be subjected to a predetermined polishing process or surface treatment so that the peripheral wall surface of the insertion hole H1 functions as a "main bearing". Such a configuration is also included in the matter of providing a "main bearing" in the insertion hole H1 of the frame 21.
In addition, in each embodiment, the case where the orbiting bearing 13 (see FIG. 1) is separate from the orbiting shaft 23c (see FIG. 1) has been described, but this is not limited thereto. For example, the peripheral wall surface of the orbiting shaft 23c may be subjected to a predetermined polishing process or surface treatment so that the peripheral wall surface of the orbiting shaft 23c functions as an "orbiting bearing". Such a configuration is also included in the matter of the orbiting scroll 23 being provided with an "orbiting bearing".

In the second embodiment (see FIG. 6), a seal member 16a is provided between the partition member 15 and the end plate 23a, and another seal member 16b is provided between the partition member 15 and the frame 21. However, this is not limiting. For example, one or both of the two seal members 16a, 16b may be omitted. Even in this configuration, the partition member 15 (see FIG. 6) can partition the space between the orbiting scroll 23 and the frame 21 into the discharge pressure space S4 and the back pressure chamber S5.

Moreover, the air conditioner W1 (see FIG. 11) described in the fourth embodiment can be applied to various types of air conditioners, such as room air conditioners, packaged air conditioners, and multi-air conditioners for buildings.
In the fourth embodiment, the air conditioner W1 (refrigeration cycle device: see FIG. 11 ) including the scroll compressor 100 has been described, but the present invention is not limited thereto. For example, the fourth embodiment can be applied to other "refrigeration cycle devices" such as a refrigerator, a hot water heater, an air-conditioning and hot water heater, a chiller, and a refrigerator.

In addition, in each of the embodiments, the scroll compressor 100 is vertically installed, but the present invention is not limited to this. For example, each of the embodiments can be applied to a configuration in which the scroll compressor 100 is horizontally or obliquely installed.
In addition, in each embodiment, a case where a refrigerant is compressed by the scroll compressor 100 has been described, but this is not limited thereto. That is, each embodiment can also be applied to a case where a predetermined gas other than a refrigerant is compressed by the scroll compressor 100.

The embodiments can be combined as appropriate. For example, the second embodiment and the fourth embodiment can be combined so that the air conditioner W1 (fourth embodiment: see FIG. 11) is equipped with a scroll compressor 100A (see FIG. 7) having the configuration described in the second embodiment. Similarly, the third embodiment can be combined with the fourth embodiment, etc.

In addition, each embodiment has been described in detail to clearly explain the present invention, and is not necessarily limited to having all of the configurations described. In addition, it is possible to appropriately add, delete, or replace part of the configuration of each embodiment with other configurations.
Furthermore, the mechanisms and configurations described above are those considered necessary for the explanation, and do not necessarily show all mechanisms and configurations of the product.

REFERENCE SIGNS LIST 100, 100A, 100B Scroll compressor 1 Sealed container 2 Compression mechanism 21 Frame 22 Fixed scroll 22a Base plate 22b Fixed wrap 23 Orbiting scroll 23a End plate 23b Orbiting wrap 23c Orbiting shaft 3 Crankshaft (shaft)
3b Upper end (end of shaft)
31b Protrusion (first fitting portion)
4 Electric motor 4a Stator 4b Rotor 12 Main bearing 13 Swing bearing 14, 14B Swing balance weight 15, 15A Partition member 15a Annular portion 15b Peripheral wall 151b Edge portion 15c Groove 17a Seal member (first seal member)
17b sealing member (second sealing member)
71 Outdoor heat exchanger 72 Outdoor fan 73 Expansion valve 74 Four-way valve 75 Indoor heat exchanger 76 Indoor fan C1, C2 Gap H1 Insertion hole H2 Eccentric hole H3 Fitting hole (second fitting portion)
S1 compression chamber S4 discharge pressure space (first region)
S5 Back pressure chamber (second region)
W1 Air conditioner (refrigeration cycle device)
Z1 central axis

Claims (9)

A sealed container;
an electric motor having a stator and a rotor and housed in the sealed container;
A shaft that rotates integrally with the rotor;
A fixed scroll having a spiral-shaped fixed wrap;
an orbiting scroll having a spiral orbiting wrap provided on an end plate, the orbiting scroll forming a compression chamber between the fixed wrap and the orbiting wrap;
an orbiting bearing that supports the shaft rotatably relative to the orbiting scroll;
a frame having an insertion hole for the shaft and supporting the fixed scroll ;
a main bearing that is installed in the insertion hole and rotatably supports an end of the shaft;
a rotating balance weight provided between the frame and the head and rotating together with the shaft;
The shaft and the swing balance weight are fitted together,
A gap is provided between the first fitting portion on the shaft side and the second fitting portion on the swing balance weight side,
The end of the shaft is provided with an eccentric hole that is eccentric with respect to a central axis of the shaft,
When the electric motor is driven, the slewing bearing comes into contact with the inner circumferential surface of the eccentric hole,
A double bearing structure in which the axial installation areas of the main bearing and the slewing bearing partially overlap,
The orbiting balance weight has an upper surface and a lower surface each having a plate shape perpendicular to a central axis of the shaft. In the orbiting scroll, the orbiting wrap is provided on one side of the end plate, and a rotation shaft is provided on the other side of the end plate,
The rotating shaft with the rotating bearing installed is fitted into the eccentric hole,
2. The scroll compressor according to claim 1, wherein the orbiting balance weight is provided radially outward of a portion of the orbiting bearing exposed through the eccentric hole. The end of the shaft is provided with a protrusion portion that protrudes toward the orbiting scroll side as the first fitting portion,
The scroll compressor according to claim 2 , wherein the orbiting balance weight is provided with a hole or a groove that fits with the protrusion as the second fitting portion. 4. The scroll compressor according to claim 3, wherein a radial length of a gap between an inner wall surface of the second fitting portion and the protrusion is longer than a radial length of a gap between the orbiting bearing and the orbiting balance weight. 2. The scroll compressor according to claim 1, further comprising a partition member that divides a space between the orbiting scroll and the frame into a first region including the insertion hole of the shaft when viewed from the direction of a central axis of the shaft, and a second region radially outward of the first region. The partition member is
An annular portion having an annular shape when viewed from the direction of the central axis of the shaft and surrounding the rotary bearing;
a peripheral wall extending from an outer circumferential edge of the annular portion toward the frame,
The scroll compressor according to claim 5, wherein an edge of the peripheral wall abuts against the frame. 7. The scroll compressor according to claim 6, wherein a groove is provided on a surface of the partition member facing the orbiting scroll and/or a surface of the end plate facing the partition member, the groove directing lubricating oil from the first region to the second region. a first annular seal member provided in a gap between the swing balance weight and the head plate,
2. The scroll compressor according to claim 1, further comprising an annular second seal member provided in a gap between the orbiting balance weight and the frame. A refrigeration cycle apparatus comprising the scroll compressor according to any one of claims 1 to 8, an outdoor heat exchanger, an expansion valve, and an indoor heat exchanger.

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