WO2023276157A1

WO2023276157A1 - Scroll compressor and refrigeration cycle device

Info

Publication number: WO2023276157A1
Application number: PCT/JP2021/025201
Authority: WO
Inventors: 遼太飯島; 和行松永
Original assignee: 日立ジョンソンコントロールズ空調株式会社
Priority date: 2021-07-02
Filing date: 2021-07-02
Publication date: 2023-01-05
Also published as: JP7466063B2; JPWO2023276157A1

Abstract

In order to provide a highly reliable scroll compressor, etc. This scroll compressor (100) comprises: a sealed container (1); an electric motor (4); a crankshaft (3); a fixed scroll (22); an orbiting scroll (23); an orbiting bearing (13) that pivotally supports the crankshaft (3) so that the crankshaft (3) is able to rotate with respect to the orbiting scroll (23); and a frame (21) that has a through-hole (H1) for the crankshaft (3) and supports the fixed scroll (22), the scroll compressor (100) further comprising an orbiting balance weight (14) provided between the frame (21) and a mirror plate (23a) and rotating with the crankshaft (3), wherein the crankshaft (3) and the orbiting balance weight (14) are fitted together, and a gap is provided between a protruding part (31b) on the crankshaft (3) side and a fitting hole on the orbiting balance weight (14) side.

Description

Scroll compressor and refrigeration cycle device

The present invention relates to scroll compressors and the like.

As a structure of a scroll compressor, a so-called double bearing structure is known, in which an orbiting scroll is provided with an orbiting shaft, an orbiting bearing is installed on the orbiting shaft, and a main bearing is installed on a frame radially outside the orbiting bearing. It is As a scroll compressor having such a double bearing structure, for example, Patent Document 1 describes that a main shaft portion with an enlarged diameter is provided on the upper portion of the shaft, and a slewing bearing is provided on this main shaft portion.

Japanese Patent No. 5018832

By adopting a double bearing structure as in Patent Document 1, the distance between the orbiting scroll and the balance weight is shortened, so the weight of the balance weight can be reduced. Deflection can be suppressed.

However, during high-speed operation, the load on the orbiting bearing increases as the centrifugal force of the orbiting scroll increases. With the technique described in Patent Literature 1, it is difficult to suppress such an increase in the load on the slewing bearing. Although it is desirable to suppress the overload on the orbiting bearing and further improve the reliability of the scroll compressor, Patent Document 1 does not describe such a technique.

Therefore, an object of the present invention is to provide a highly reliable scroll compressor and the like.

In order to solve the above-described problems, a scroll compressor according to the present invention includes a closed container, a stator and a rotor, an electric motor housed in the closed container, and a shaft that rotates integrally with the rotor. a fixed scroll having a spiral stationary wrap; an orbiting scroll having a spiral orbiting wrap provided on an end plate and forming a compression chamber between the stationary wrap and the orbiting wrap; an orbiting bearing that rotatably supports the orbiting scroll; and a frame that has an insertion hole for the shaft and supports the fixed scroll. A swivel balance weight that rotates together with a shaft is provided, the shaft and the swivel balance weight are fitted together, and a first fitting portion on the shaft side and a second fitting portion on the swivel balance weight side. A gap was provided between them.

According to the present invention, a highly reliable scroll compressor and the like can be provided.

1 is a longitudinal sectional view of a scroll compressor according to a first embodiment; FIG. FIG. 2 is a cross-sectional view of the scroll compressor according to the first embodiment taken along line II-II of 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 showing the force generated in each member by partially enlarging the region K1 shown in FIG. 1 in the scroll compressor according to the first embodiment; It is an explanatory view showing relation between rotation speed of a scroll compressor concerning a 1st embodiment, and load. 1. It is the longitudinal cross-sectional view which expanded the part corresponded to the area|region K1 shown in FIG. 1 in the scroll compressor which concerns on 2nd Embodiment. FIG. 8 is an exploded perspective view including the orbiting scroll, orbiting bearing, orbiting balance weight, partition member, seal member, and upper end portion of the crankshaft of the scroll compressor according to the second embodiment. FIG. 8 is a perspective view of a partition member of a scroll compressor according to a modified example of the second embodiment; 1. It is the longitudinal cross-sectional view which expanded the part corresponded to the area|region K1 shown in FIG. 1 in the scroll compressor which concerns on 3rd Embodiment. 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. 11 is a configuration diagram of a refrigerant circuit of an air conditioner according to a fourth embodiment;

<<First embodiment>>
<Structure of scroll compressor>
FIG. 1 is a longitudinal sectional view of a scroll compressor 100 according to the first embodiment.
A scroll compressor 100 shown in FIG. 1 is a device that compresses gaseous refrigerant. As shown in FIG. 1, the scroll compressor 100 includes a closed container 1, a compression mechanism section 2, a crankshaft 3 (shaft), an electric motor 4, an Oldham ring 5, and

balance weights

6a and 6b. ing. Further, the scroll compressor 100 includes a fixed member 7, a subframe 8, a lower bearing 9, a leg 10, a power terminal 11, a main bearing 12, a turning bearing 13, and a turning A balance weight 14 is provided.

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

As shown in FIG. 1, a suction pipe P1 is inserted into and fixed to the lid chamber 1b of the sealed container 1. The suction pipe P<b>1 is a pipe that guides the refrigerant to the suction port J<b>1 of the compression mechanism section 2 . A discharge pipe P2 is inserted and fixed at a predetermined position below the frame 21 in the cylindrical chamber 1a of the sealed container 1. As shown in FIG. The discharge pipe P<b>2 is a pipe that guides the refrigerant compressed by 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 section 2 includes a frame 21 , a fixed scroll 22 and an orbiting scroll 23 , and is arranged in the upper space inside 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 an orbiting scroll 23 described below. The fixed scroll 22 is installed above the frame 21 and fastened to the frame 21 with bolts 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 plan view. In addition, in order to secure a region S2 (a circular region in a bottom view) in which the turning wrap 23b turns with respect to the fixed wrap 22b, the vicinity of the center of the lower surface of the base plate 22a is recessed upward by a predetermined amount. A suction port J1 for introducing the refrigerant through the suction pipe P1 is provided in the base plate 22a.
The fixing wrap 22b has a spiral shape and extends downward from the base plate 22a in the region S2. The bottom surface of the base plate 22a (the bottom surface of the radially outer portion of the region S2) and the bottom end of the fixing 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 includes a disk-shaped end plate 23a, a spiral orbiting wrap 23b erected on the end plate 23a, and a turning shaft 23c extending downward from near the center of the end plate 23a. That is, in the orbiting scroll 23, an orbiting wrap 23b is provided on the upper side (one side) of the end plate 23a, and a turning shaft 23c is provided on the lower side (the other side) of the end plate 23a.

The orbiting wrap 23b is a member that forms the compression chamber S1 together with the fixed wrap 22b. The turning shaft 23c has a columnar shape and is fitted into the eccentric hole H2 of the upper end portion 3b of the crankshaft 3. As shown in FIG. The spiral fixed wrap 22b and the spiral swirl wrap 23b are meshed to form a compression chamber S1 between the fixed wrap 22b and the swirl wrap 23b. The compression chambers S1 are spaces for compressing gaseous refrigerant, and are formed on the outer line side and the inner line side of the orbiting wrap 23b. A discharge port J2 is provided in the vicinity of 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 inside the sealed container 1. As shown in FIG.

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

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

Also, the swivel shaft 23c with the swivel bearing 13 installed is fitted in the eccentric hole H2. A small radial gap is provided between the inner peripheral surface of the eccentric hole H2 and the orbiting bearing 13 so that lubricating oil can enter. As the electric motor 4 is driven, the turning shaft 23c rotates eccentrically with respect to the main shaft portion 3a.

The upper end 3b (end) of the crankshaft 3 (shaft) is provided with a projection 31b (see also FIG. 2) projecting upward (toward the orbiting scroll 23) as a "first fitting portion". Although the details will be described later, the protrusion 31b is fitted into the fitting hole H3 (not shown in FIG. 1, see FIG. 2) of the turning balance weight 14. As shown in FIG.

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 sucks up lubricating oil from the oil reservoir R1 of the sealed container 1, and elongates downward from the lower shaft portion 3c. A positive displacement pump, a centrifugal pump, or the like may be provided in the oil supply piece 3d.

As shown in FIG. 1, the crankshaft 3 (that is, 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 the lubricating oil. The lubricating oil stored as the oil reservoir R1 in the sealed container 1 rises through the oil supply passage 3e and is guided to the eccentric hole H2 of the upper end portion 3b. Further, the oil supply passage 3e is branched in a predetermined manner so that the lubricating oil is also supplied to the lower bearing 9, the main bearing 12, the orbiting bearing 13, and the like.

The electric motor 4 is a drive source that rotates the crankshaft 3 and is provided between the frame 21 and the sub-frame 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 windings 41a and is fixed to the inner peripheral surface of the cylinder chamber 1a. The rotor 4b is rotatably arranged radially inside the stator 4a. The crankshaft 3 is fixed to the rotor 4b by press fitting or the like so as to be 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. 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 installed in a groove (not shown) formed in the frame 21. .

Balance weights

6 a and 6 b are members for suppressing vibration of scroll compressor 100 . In the example of FIG. 1, a balance weight 6a is installed on the upper side of the rotor 4b in the main shaft portion 3a, and another balance weight 6b is installed on the lower surface of the rotor 4b.

The fixing member 7 is a member that fixes the position of the sub-frame 8, and is fixed to the inner peripheral surface of the closed 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 fixed member 7 with bolts B2. The sub-frame 8 is provided with a hole (not shown) through which the crankshaft 3 is inserted. The lower bearing 9 rotatably supports the lower shaft portion 3 c of the crankshaft 3 and is installed on the inner peripheral surface of the hole of the sub-frame 8 .

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

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

As shown in FIG. 1, the installation areas of the main bearing 12 and the orbiting bearing 13 partially overlap in the axial direction. By adopting such a double bearing structure, the axial distance between the point of action of the force from the main bearing 12 to the crankshaft 3 and the point of action of the force from the swivel bearing 13 to the crankshaft 3 is reduced. can be shortened. Therefore, it is possible to suppress the occurrence of a moment that causes the crankshaft 3 to tilt, thereby suppressing deflection and uneven contact of the crankshaft 3 . Moreover, since the length of the crankshaft 3 can be shortened by adopting the double bearing structure, it is possible to reduce the size and cost of the scroll compressor 100 .

The turning balance weight 14 shown in FIG. 1 is a member for reducing the load acting on the turning bearing 13, and is provided between the frame 21 and the end plate 23a. That is, the orbiting balance weight 14 is installed so as to fit in the space between the frame 21 and the orbiting scroll 23 . To explain the positional relationship of the turning balance weight 14 from another point of view, it can be said that the turning balance weight 14 is 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 in the eccentric hole H2, but the upper end of the swivel bearing 13 is exposed from the eccentric hole H2. A swivel balance weight 14 is provided radially outside the portion (upper end portion of the swivel bearing 13) where the swivel bearing 13 is exposed from the eccentric hole H2. A configuration including such a swing balance weight 14 will be described in detail with reference to FIG.

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

As shown in FIG. 2, the turning balance weight 14 is provided with a circular hole H4 in a cross-sectional view with the central axis Z2 of the turning shaft 23c as a reference. The diameter of the hole H<b>4 of the turning balance weight 14 is slightly larger than the outer diameter of the turning bearing 13 . That is, between the inner peripheral surface of the hole H4 of the swivel balance weight 14 and the outer peripheral surface of the swivel bearing 13, a minute gap (not shown) is provided in the radial direction. By providing such a minute gap, the turning balance weight 14 is relatively movable in the circumferential direction with respect to the turning shaft 23 c and the turning bearing 13 . In other words, the swivel balance weight 14 is rotatably supported by the swivel bearing 13 .

The swivel balance weight 14 has a semicircular plummet 14a in a cross-sectional view in a region opposite to the "eccentric side" of the swivel shaft 23c. The "eccentric side" of the turning shaft 23c (that is, the eccentric side of the eccentric hole H2 in FIG. 1) means that the central axis Z2 of the turning shaft 23c is eccentric with respect to the central axis Z1 of the crankshaft 3. side (the right side of the paper surface of FIG. 2). That is, the center of gravity G1 of the turning balance weight 14 is located on the opposite side of the center axis Z2 of the turning shaft 23c with the center axis Z1 of the crankshaft 3 as a reference. As a result, part of the centrifugal force of the orbiting scroll 23 is offset by the orbiting balance weight 14, so the load on the orbiting bearing 13 can be reduced.

Also, the crankshaft 3 (shaft) and the turning balance weight 14 are fitted. That is, the weight portion 14a of the turning balance weight 14 has 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. Department”. Moreover, there is a gap between the protrusion 31b that is the "first fitting portion" on the crankshaft 3 (shaft) side and the fitting hole H3 that is the "second fitting portion" on the turning balance weight 14 side. is provided. More specifically, as shown in FIG. 2, radial gaps C1 and C2 are formed between the inner wall surface of the fitting hole H3 and the protrusion 31b with the center axis Z1 of the crankshaft 3 as a reference (center). is provided. A gap C1 on the radially outer side of the protrusion 31b and a gap C2 on the radially inner side of the protrusion 31b are minute gaps (symbol not shown).

In other words, the gaps C1 and C2 between the inner wall surface of the fitting hole H3 (second fitting portion) and the protrusion 31b are longer than the radial length of the gap between the swivel bearing 13 and the swivel balance weight 14. are longer in the radial direction. 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 manner, a radial force is directly applied to the orbiting bearing 13 from the orbiting balance weight 14 .
Also in the circumferential direction with the center axis Z1 of the crankshaft 3 as a reference (center), a slight gap is provided between the inner wall surface of the fitting hole H3 and the protrusion 31b. 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 (horizontal direction including radial direction and circumferential direction) perpendicular to the central axis Z1 of the crankshaft 3. It is

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. FIG.
3, the orbiting scroll 23 and orbiting bearing 13 are shown cut along a predetermined plane (not shown) including the center axis Z1 of the crankshaft 3 (see FIG. 1).
As described above, the upper end portion 3b of the crankshaft 3 is provided with the projecting portion 31b projecting upward. On the other hand, the turning balance weight 14 is provided with a fitting hole H3 into which the protrusion 31b is fitted.

When the crankshaft 3 rotates with the driving of the electric motor 4 (see FIG. 1), the projection 31b moves in the circumferential direction, so that the inner wall surface of the fitting hole H3 moves in the circumferential direction (the tangential line when the projection 31b rotates). direction) (see also FIG. 2). As a result, the turning balance weight 14 rotates together with the crankshaft 3 . In other words, the turning balance weight 14 rotates synchronously (rotates so that the rotation angle becomes equal) integrally with the crankshaft 3 .

Further, when the crankshaft 3 is rotated by driving the electric motor 4 shown in FIG. 1, the turning shaft 23c fitted in the eccentric hole H2 of the upper end portion 3b turns accordingly. As a result, the compression chamber S1 between the fixed scroll 22 and the orbiting scroll 23 is contracted to compress the refrigerant. The compressed refrigerant is discharged into the upper space S3 inside 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 closed vessel 1 and the compression mechanism 2, and further , is discharged to the outside of the sealed container 1 through the discharge pipe P2.

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

Here, since 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, the increase in the centrifugal force Fcos of the orbiting scroll 23 is particularly noticeable in the high speed range. Therefore, in the conventional configuration in which the orbital balance weight 14 is not provided, if the upper limit speed of the scroll compressor is increased, there is a possibility that the orbital bearing 13 will be overloaded. In addition, in the conventional configuration, the oil film thickness on the outer peripheral side of the slewing bearing 13 becomes thin, especially in the high speed range, and the friction coefficient associated with the direct contact between the inner peripheral surface of the eccentric hole H2 and the slewing bearing 13 increases. , the slewing bearing 13 and the like may be worn or seized.

On the other hand, 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 on the side opposite to the orbiting shaft 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 having 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 of the centrifugal force.

FIG. 5 is an explanatory diagram showing the relationship between the rotation speed and the load of the scroll compressor (see also FIG. 4 as appropriate).
Note that the horizontal axis of FIG. 5 is the rotation speed of the scroll compressor 100 (that is, the rotation speed of the electric motor 4), and the vertical axis is the load. The dashed-dotted line in FIG. 5 is the horizontal gas load Fg accompanying the compression of the refrigerant. A dashed line in FIG. 5 represents the centrifugal force Fcos acting on the orbiting scroll 23 . The white arrow in FIG. 5 represents the centrifugal force Fcob acting on the turning balance weight 14 . The solid line in FIG. 5 is the load Fr acting on the orbiting bearing 13 as the reaction force of the centrifugal force.

As shown in FIG. 5, the gas load Fg associated with refrigerant compression is substantially 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 rotational speed of the scroll compressor 100 . If the swivel balance weight 14 were not provided, the sum of the gas load Fg and the centrifugal force Fcos would act on the swivel bearing 13, which could overload the swivel bearing 13 in the high speed range.

On the other hand, 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 of the centrifugal force is calculated from the centrifugal force Fcos of the orbiting scroll 23 by the orbiting balance weight The value is obtained by subtracting the centrifugal force Fcob of 14 (Fr=Fcos-Fcob). The sum of this load Fr and the gas load Fg acts on the turning bearing 13 . Therefore, particularly in a high speed region where the centrifugal force of the orbiting scroll 23 increases, the load applied to the orbiting bearing 13 can be greatly reduced. Note that the space between the orbiting scroll 23 and the frame 21 is filled with the lubricating oil after the main bearing 12 and the orbiting bearing 13 have been lubricated. That is, since an oil film is formed between the inner peripheral surface of the hole H4 (see FIG. 2) of the turning balance weight 14 and the turning bearing 13, a good lubricating state is maintained.

<effect>
According to the first embodiment, the protrusion 31b (first fitting portion: see FIG. 2) of the crankshaft 3, the fitting hole H3 (second fitting portion: see FIG. 2) of the turning balance weight 14, A gap (clearances C1, C2, etc. in FIG. 2) is provided between the . Therefore, when the projection 31b presses the wall surface of the fitting hole H3 in the circumferential direction to rotate the turning balance weight 14, the turning balance weight 14 moves radially within the range of the gap due to the centrifugal force. It contacts the swivel bearing 13 . As a result, 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 in the orbiting bearing 13 . As a result, the load applied to the orbiting bearing 13 can be significantly reduced particularly in a high speed range where the centrifugal force of the orbiting scroll 23 increases. In addition, since a sufficient film thickness of the lubricating oil is ensured in the orbiting bearing 13, the friction loss of the orbiting bearing 13 can be reduced, and wear and seizure of the orbiting bearing 13 can be suppressed.

In addition, it is possible to increase the upper limit of the rotation speed of the scroll compressor 100 (further increase the speed) while ensuring the reliability of the orbiting bearing 13 . Thus, according to the first embodiment, the scroll compressor 100 with high performance and high reliability can be provided. A turning balance weight 14 is provided between the turning scroll 23 and the frame 21 so that the centrifugal force of the turning balance weight 14 directly acts on the turning bearing 13 . As a result, the load applied to the orbiting bearing 13 can be reduced, and the deflection of the crankshaft 3 can be suppressed.

<<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. configuration, etc.: see FIG. 1) are the same as in the first embodiment. Therefore, the portions different from the first embodiment will be described, and the description of the overlapping portions will be omitted.

FIG. 6 is an enlarged vertical cross-sectional view of a portion corresponding to the region K1 shown in FIG. 1 in the scroll compressor 100A according to the second embodiment.
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 configuration described in the first embodiment.
The partition member 15 defines a discharge pressure space S4 (first discharge pressure space S4) including the insertion hole H1 of the crankshaft 3 when the space between the orbiting scroll 23 and the frame 21 is viewed from the direction of the center axis Z1 of the crankshaft 3 (shaft). region) and a back pressure chamber S5 (second region) radially outside the discharge pressure space S4. As shown in FIG. 6 , the partition member 15 is provided between the orbiting scroll 23 and the frame 21 . A swivel balance weight 14 is provided inside the partition member 15 .

Lubricating oil after lubricating the main bearing 12, the orbiting bearing 13 and the like flows into the discharge pressure space S4 inside the partition member 15. This lubricating oil has substantially the same discharge pressure as the refrigerant compressed by the compression mechanism portion 2 . Therefore, the pressure in the discharge pressure space S4 is substantially equal to the discharge pressure described above. Further, when the pressure in the back pressure chamber S5 becomes lower than that in the discharge pressure space S4, the pressure difference between the discharge pressure space S4 and the back pressure chamber S5 is maintained because the partition member 15 separates the discharge pressure space S4 and the back pressure chamber S5. be done.

The pressure (back pressure) in the back pressure chamber S5 can be controlled, for example, by intermittently communicating the compression chamber S1 and the back pressure chamber S5 with the movement of the orbiting scroll 23, or by providing a back pressure valve (not shown). can be adjusted by By providing such a back pressure chamber S5, it is possible to prevent the force that presses 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, orbiting bearing 13, orbiting balance weight 14, partition member 15, seal member 16a, and upper end portion 3b of the crankshaft 3 of the scroll compressor 100A.
7, the orbiting scroll 23 and orbiting bearing 13, as well as the partition member 15 and the seal member 16a, are cut along a predetermined plane (not shown) including the central axis line Z1 (see FIG. 6) of the crankshaft 3. Illustrates things. 7, illustration of the seal member 16b (see FIG. 6) inside the partition member 15 is omitted.

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

A seal member 16a shown in FIG. 6 is a member made of resin that closes a minute 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 FIG. 6, an annular groove M1 is formed in the lower surface of the end plate 23a, and the seal member 16a is installed in this groove M1. The sealing member 16a is vertically compressed by the partition member 15 and the end plate 23a.

As shown in FIG. 6, the frame 21 has an annular thick portion 21a in plan view in a portion including the peripheral wall surface of the insertion hole H1. The thick portion 21a is formed to be thicker in the axial direction than the outer peripheral side thereof, and protrudes upward (toward the orbiting scroll 23).

A seal member 16b shown in FIG. 6 is a member made of resin that closes a minute gap between the peripheral wall 15b of the partition member 15 and the thick portion 21a of the frame 21. In the example of FIG. 6, an annular groove M2 is formed in the outer peripheral surface of the thick portion 21a of the frame 21, and the seal member 16b is installed in this groove M2. The partition member 15 and the frame 21 compress the sealing member 16b in the radial direction. By providing these

seal members

16a and 16b, leakage of refrigerant from the inside to the outside of the partition member 15 can be suppressed.

<effect>
According to the second embodiment, the partition member 15 (see FIG. 6) partitions the space between the orbiting scroll 23 and the frame 21 into the discharge pressure space S4 and the back pressure chamber S5. As a result, for example, even with a structure in which the discharge pressure acts on the lower end of the crankshaft 3, it is possible to prevent the crankshaft 3 from floating due to the differential pressure between the upper and lower sides. Further, by adjusting the pressure (back pressure) of the back pressure chamber S5, the thrust load (load in the axial direction) when pressing the orbiting scroll 23 against the fixed scroll 22 can be reduced. As a result, the friction loss of the compression mechanism portion 2 can be reduced, and wear and seizure can be suppressed.

<<Modification of Second Embodiment>>
In the second embodiment, the configuration in which the partition member 15 (see FIG. 7) is not particularly provided with grooves has been described, but the configuration is not limited to this. For example, as described below, a radial groove 15c may be provided in the upper surface of the annular portion 15a of the partition member 15A (see FIG. 8), and the lubricating oil may flow through this groove 15c.

FIG. 8 is a perspective view of a partition member 15A of a scroll compressor according to a modification of the second embodiment.
In the modified example of FIG. 8, a groove 15c is provided on the upper surface of the annular portion 15a of the partition member 15A. More specifically, a groove 15c extending from the inner peripheral edge to the outer peripheral edge of the annular portion 15a is provided in the radial direction. The 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 the minute grooves 15c on the upper surface of the partition member 15A in this manner, the lubricating oil flowing from the discharge pressure space S4 (see FIG. 6) is squeezed by the grooves 15c and then ). As a result, for example, the pressure (back pressure) of the back pressure chamber S5 can be adjusted by appropriately adjusting the channel cross-sectional area of the groove 15c at the design stage. Although FIG. 8 shows an example in which one groove 15c is provided, a plurality of grooves may be provided.

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

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

<<Third Embodiment>>
The third embodiment differs from the second embodiment in that two sealing

members

17a and 17b (see FIG. 9) are provided instead of the partition wall member 15A (see FIG. 6). Points (such as the overall configuration of the scroll compressor) are the same as in the second embodiment. Therefore, the parts different from the second embodiment will be explained, and the explanation of overlapping parts will be omitted.

FIG. 9 is an enlarged longitudinal sectional view of a portion corresponding to the region K1 shown in FIG. 1 in the scroll compressor 100B according to the third embodiment.
As shown in FIG. 9, the scroll compressor 100B has two

seal members

17a and 17b installed on the orbital balance weight 14B. These

seal members

17a and 17b divide the space between the orbiting scroll 23 and the frame 21 in the radial direction into a discharge pressure space S4 (first region) including an insertion hole H1 for the crankshaft 3 (shaft) and a discharge pressure space S4 (first region). It is a member made of resin that partitions into a back pressure chamber S5 (second region) on the radially outer side of the pressure space S4.

FIG. 10 is an exploded perspective view including the orbiting scroll 23, orbiting bearing 13, orbiting balance weight 14B,

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 in the upper surface of the swing balance weight 14B. An annular seal member 17a (first seal member) is installed in the groove M3. As shown in FIG. 9, the annular seal member 17a is provided in the gap between the turning balance weight 14B and the end plate 23a.

On the other hand, an annular groove M4 (see FIG. 9) is also formed on the lower surface of the turning balance weight 14B. An annular seal member 17b (second seal member) is installed in the 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. As shown in FIG. 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 turning balance weight 14B is longer than in the first embodiment (see FIG. 3).

While the scroll compressor 100B is being driven, the orbiting balance weight 14B and the

seal members

17a and 17b are integrally moved (rotated) in the circumferential direction. That is, one seal member 17a moves in the circumferential direction together with the orbiting balance weight 14B while being vertically compressed between the orbiting balance weight 14B and the orbiting scroll 23 . The other seal member 17b moves in the circumferential direction together with the rotating balance weight 14B while being vertically compressed between the rotating balance weight 14B and the frame 21 .

<effect>
According to the third embodiment, two sealing

members

17a and 17b are provided to divide the space between the orbiting scroll 23 and the frame 21 into a discharge pressure space S4 (see FIG. 9) and a back pressure chamber S5 (see FIG. 9). ) can be divided into Moreover, unlike the second embodiment, the radial size of the turning 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, it is possible to sufficiently secure the outer diameter of the turning balance weight 14B. As a result, the load on the orbiting bearing 13 can be further reduced, and the performance and reliability of the scroll compressor 100B can be improved.

<<Modification of Third Embodiment>>
Although the case where the two

seal members

17a and 17b are provided in the turning balance weight 14B has been described in the third embodiment, the present invention is not limited to this. 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 installed in this groove. Alternatively, 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 installed in this groove. Even with such a configuration, the same effects as those of the third embodiment can be obtained.

Further, grooves (not shown) for guiding lubricating oil from the discharge pressure space S4 to the back pressure chamber S5 are formed on the lower surface of the end plate 23a of the orbiting scroll 23 (the surface on the side of the orbiting balance weight 14) and the upper surface of the frame 21 (orbiting surface facing the balance weight 14). Accordingly, the pressure (back pressure) of the back pressure chamber S5 can be adjusted by appropriately adjusting the channel 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 the refrigerant circuit Q1 of the air conditioner W1 according to the fourth embodiment.
The solid line arrows in FIG. 11 indicate the flow of the refrigerant during the heating operation.
On the other hand, dashed arrows in FIG. 11 indicate the flow of the refrigerant during the 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, an indoor fan 76 and .

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 gaseous refrigerant, and has the same configuration as the first embodiment (see FIG. 1). The outdoor heat exchanger 71 is a heat exchanger that exchanges heat between a refrigerant flowing through its heat transfer tubes (not shown) and outside air sent 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 provided with an outdoor fan motor 72a as a driving source, and is installed near the outdoor heat exchanger 71. As shown in FIG.

The indoor heat exchanger 75 is a heat exchanger in which heat is exchanged between the refrigerant flowing through the heat transfer tube (not shown) and the indoor air (air-conditioned room air) sent from the indoor fan 76 . be. The indoor fan 76 is a fan that sends indoor air to the indoor heat exchanger 75 . The indoor fan 76 is provided with an indoor fan motor 76 a as a drive 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 decompressed by the expansion valve 73 is guided to an "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 according to the operation mode of the air conditioner W1. For example, during cooling operation (see the dashed arrow in FIG. 11), in the refrigerant circuit Q1, the scroll compressor 100, the outdoor heat exchanger 71 (condenser), the expansion valve 73, and the indoor heat exchanger 75 (evaporator ) in sequence, the refrigerant circulates. On the other hand, during heating operation (see the solid line arrow in FIG. 11), in the refrigerant circuit Q1, 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, devices such as the expansion valve 73, the four-way valve 74, and the indoor fan 76 are controlled in a predetermined manner by a controller (not shown).

<effect>
According to the fourth embodiment, the air conditioner W1 includes the scroll compressor 100 having the same configuration as in the first embodiment. As a result, the performance and reliability of the air conditioner W1 as a whole can be improved.

<<Modification>>
Although the scroll compressor 100 and the air conditioner W1 according to the present invention have been described above in each embodiment, the present invention is not limited to these descriptions, and various modifications can be made.
For example, in each embodiment, the scroll compressor 100 and the like (see FIG. 1) having a double bearing structure have been described, but the present invention is not limited to this. That is, in the orbiting scroll 23, an orbiting wrap 23b is provided on the upper side (one side in the axial direction) of the end plate 23a, and a boss portion (not shown) is provided on the lower side (the other side in the axial direction) of the end plate 23a to An eccentric portion (not shown) of the shaft 3 may be fitted into a concave portion of the boss portion. In such a configuration, the turning balance weight 14 is provided between the frame 21 and the end plate 23 a and rotates together with the crankshaft 3 . Note that the crankshaft 3 (shaft) and the turning balance weight 14 are fitted together, and the "first fitting portion" on the crankshaft 3 side, the "second fitting portion" on the turning balance weight 14 side, It is assumed that a predetermined gap (for example, a gap in a direction perpendicular to the center axis of the crankshaft 3) is provided between them. It is also assumed that the center of gravity of the turning 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 such a configuration, the load acting on the orbiting bearing 13 as the reaction force of the centrifugal force can be reduced, so the performance and reliability of the scroll compressor can be improved. Further, it is possible to apply the second embodiment to such a configuration, and it is also possible to apply the third embodiment and the fourth embodiment.

Further, in each embodiment, a fitting hole H3 (second fitting portion) is provided in the turning balance weight 14 (see FIG. 2), and the projection portion 31b (first fitting portion) of the crankshaft 3 is provided in the fitting hole H3. Although the configuration in which the portion ) is fitted has been described, the configuration is not limited to this. For example, a fitting groove (second fitting portion: not shown) is provided as a groove that fits into the turning balance weight 14, and the projection portion 31b (first fitting portion) of the crankshaft 3 is provided in this fitting groove. may be fitted. In other words, the turning balance weight 14 may be provided with a “second fitting portion” that is a hole or groove that fits into the protrusion 31b.

A projection (second fitting portion, not shown) extending axially downward (toward the frame 21 side) is provided on the turning balance weight 14, and a fitting hole or fitting groove (not shown) in which the projection is fitted is provided. A first fitting portion (not shown) may be provided at the upper end portion 3 b of the crankshaft 3 . In such a configuration, a gap (for example, a clearance in the vertical direction) may be provided. Even with such a configuration, the same effects as those of each embodiment can be obtained.
Also, in each embodiment, the case where the main bearing 12 (see FIG. 1) and the frame 21 (see FIG. 1) are separate bodies has been described, but the present invention is not limited to this. 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 fact that the "main bearing" is provided in the insertion hole H1 of the frame 21. As shown in FIG.
Moreover, although each embodiment demonstrated the case where the turning bearing 13 (refer FIG. 1) was the turning shaft 23c (refer FIG. 1) and another body, it does not restrict to this. For example, the peripheral wall surface of the rotating shaft 23c may be made to function as a "swivel bearing" by subjecting the peripheral wall surface of the rotating shaft 23c to a predetermined polishing process or surface treatment. Such a configuration is also included in the matter that the orbiting scroll 23 is provided with the "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. Illustrated, but not limited to. For example, one or both of the two

seal members

16a and 16b may be omitted. Even with such a configuration, the space between the orbiting scroll 23 and the frame 21 can be partitioned into the discharge pressure space S4 and the back pressure chamber S5 by the partition member 15 (see FIG. 6).

Also, 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, package air conditioners, and multi air conditioners for buildings.
Moreover, in the fourth embodiment, the air conditioner W1 (refrigerating cycle device: see FIG. 11) including the scroll compressor 100 has been described, but the present invention is not limited to this. For example, the fourth embodiment can be applied to other "refrigerating cycle devices" such as refrigerators, water heaters, air-conditioning water heaters, chillers, and refrigerators.

Moreover, although each embodiment demonstrated the structure by which the scroll compressor 100 was vertically installed, it does not restrict to this. For example, each embodiment can be applied to a configuration in which the scroll compressor 100 is installed horizontally or diagonally.
Moreover, although each embodiment demonstrated the case where the refrigerant|coolant was compressed with the scroll compressor 100, it does not restrict to this. That is, each embodiment can also be applied when a predetermined gas other than refrigerant is compressed by the scroll compressor 100 .

Also, each embodiment can be combined as appropriate. For example, by combining the second embodiment and the fourth embodiment, the air conditioner W1 (fourth embodiment: see FIG. 11) includes the scroll compressor 100A (see FIG. 7) having the configuration described in the second embodiment. You may prepare. Similarly, combinations of the third embodiment and the fourth embodiment, etc. are also possible.

Moreover, each embodiment is described in detail in order to explain the present invention in an easy-to-understand manner, and is not necessarily limited to those having all the described configurations. Moreover, it is possible to appropriately add, delete, or replace a part of the configuration of each embodiment with another configuration.
Further, the mechanisms and configurations described above show those considered necessary for explanation, and do not necessarily show all the mechanisms and configurations on the product.

Reference Signs List

100, 100A, 100B Scroll Compressor 1 Sealed Container 2 Compression Mechanism Part 21 Frame 22 Fixed Scroll 22a Base Plate 22b Fixed Wrap 23 Orbiting Scroll

23a End Plate

23b Orbiting Wrap

23c Orbiting Axis 3 Crankshaft (Shaft)
3b upper end (end of shaft)
31b projection (first fitting portion)
4 electric motor 4a stator 4b rotor 12 main bearing 13 swivel bearing 14, 14B

swivel balance weight

15, 15A partition member 15a annular portion 15b peripheral wall 151b edge 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 fans 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 area)
W1 Air conditioner (refrigeration cycle device)
Z1 center axis

Claims

a closed container;
an electric motor having a stator and a rotor and housed in the closed container;
a shaft that rotates integrally with the rotor;
a stationary scroll having a spiral stationary wrap;
an orbiting scroll having a spiral orbiting wrap provided on the end plate and forming a compression chamber between the fixed wrap and the orbiting wrap;
an orbiting bearing that rotatably supports the shaft with respect to the orbiting scroll;
a frame having an insertion hole for the shaft and supporting the fixed scroll;
A turning balance weight provided between the frame and the end plate and rotating together with the shaft,
The shaft and the turning balance weight are fitted together,
A scroll compressor in which a gap is provided between a first fitting portion on the shaft side and a second fitting portion on the turning balance weight side.
In the orbiting scroll, the orbiting wrap is provided on one side of the end plate, and the orbiting shaft is provided on the other side of the end plate,
An end of the shaft is provided with an eccentric hole that is eccentric with respect to the central axis of the shaft,
The swivel shaft with the swivel bearing installed is fitted in the eccentric hole,
The scroll compressor according to claim 1, wherein the orbital balance weight is provided radially outside a portion where the orbital bearing is exposed from the eccentric hole.
The end portion of the shaft is provided with a protrusion projecting toward the orbiting scroll as the first fitting portion,
The scroll compressor according to claim 2, wherein the orbiting balance weight is provided with a hole or groove that fits into the protrusion as the second fitting portion.
The radial length of the gap between the inner wall surface of the second fitting portion and the protrusion is longer than the radial length of the gap between the swivel bearing and the swivel balance weight. The scroll compressor according to claim 3, characterized by:
The space between the orbiting scroll and the frame includes a first region including the insertion hole of the shaft when viewed from the direction of the central axis of the shaft, and a second region radially outward of the first region, 2. The scroll compressor according to claim 1, further comprising a partition wall member that partitions the compressor.
The partition member is
an annular portion that has an annular shape when viewed from the direction of the central axis of the shaft and surrounds the slewing bearing;
a peripheral wall extending from the outer peripheral edge of the annular portion toward the frame;
The scroll compressor according to claim 5, wherein the edge of the peripheral wall is in contact with the frame.
The orbiting scroll side surface of the partition member and/or the partition member side surface of the end plate are provided with grooves for guiding lubricating oil from the first region to the second region. The scroll compressor according to claim 6.
An annular first seal member provided in a gap between the swivel balance weight and the end plate,
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, and an outdoor heat exchanger, an expansion valve, and an indoor heat exchanger.