JP2022019027A - Scroll compressor and refrigeration cycle device - Google Patents

Abstract

To provide a scroll compressor etc. which achieves high reliability with a simple structure.SOLUTION: A scroll compressor 100 includes: a closed container 1; a fixed scroll 21; a revolving scroll 22; a frame 23; an electric motor 6; a crank shaft 3; a discharge pipe Pb; and an oil ring 13. A peripheral end surface of a lid chamber 1b closely contacts with a lid chamber 1b side surface in a flange part 212a of a base plate 21a and grooves recessed to the radial inner side are provided at the flange part 212a of the base plate 21a and a peripheral edge part 23a of the frame 23. A space between the base plate 21a and the lid chamber 1b and a space between the frame 23 and the electric motor 6 communicate with each other through clearances of the grooves. In an area near an upper end of the groove, a part of the clearance is blocked by the lid chamber 1b.SELECTED DRAWING: Figure 1

Description

The present invention relates to a scroll compressor and the like.

As a technique for simplifying the configuration by eliminating the need for bolts for fastening the fixed scroll of the scroll compressor and the frame, for example, the technique described in Patent Document 1 is known. That is, Patent Document 1 describes a scroll compressor in which the shell upper lid is hermetically fixed to the inner peripheral surface of the shell body and the fixed scroll is sandwiched between the peripheral end surface of the shell upper lid and the frame. There is.

Japanese Unexamined Patent Publication No. 7-174079

By the way, the scroll compressor is provided with a gas flow path for guiding the refrigerant discharged into the space between the fixed scroll and the shell upper lid to the motor chamber on the lower side of the frame. As described above, the scroll compressor described in Patent Document 1 has a configuration in which a fixed scroll is sandwiched between the peripheral end surface of the shell upper lid and the frame. In such a configuration, a part of the gas flow path is blocked by the lower end surface of the shell upper lid, and the cross-sectional area of the gas flow path becomes small. Rise. Further, the refrigerant flowing out to the motor chamber through the gas flow path is agitated as the motor rotates. As a result, the mist-like lubricating oil mixed in the refrigerant is scattered in the motor chamber, so that the lubricating oil easily flows out through the discharge pipe.

If a large amount of lubricating oil flows out through the discharge pipe, the efficiency of the refrigeration cycle is lowered, and the lubricity and sealing property of each sliding portion of the scroll compressor are lowered. It is desirable to achieve both simplification of the configuration of the scroll compressor and improvement of reliability, but such a technique is not described in Patent Document 1.

Therefore, it is an object of the present invention to provide a highly reliable scroll compressor or the like with a simple configuration.

In order to solve the above-mentioned problems, the scroll compressor according to the present invention has a cylindrical tubular chamber, a lid chamber that closes the upper side of the tubular chamber, and a bottom chamber that closes the lower side of the tubular chamber. A swivel scroll having a closed container, a base plate fixed to the cylindrical chamber, a fixed scroll having a spiral fixed wrap, and a swirling swivel wrap forming a compression chamber together with the fixed wrap, and the swivel scroll. It is provided with a frame supporting the frame, an electric motor having a stator and a rotor, and a drive shaft having a through hole for guiding lubricating oil and rotating integrally with the rotor, and is installed in the cylinder chamber thereof. It includes a discharge pipe having one end located inside the closed container and the other end located outside the closed container, and a partition wall installed in the frame and separating the one end of the discharge pipe from the cylindrical chamber. The peripheral end surface of the lid chamber is in close contact with the surface of the flange portion of the base plate on the lid chamber side, or a part of the inner wall surface of the lid chamber is placed on the surface of the flange portion of the base plate on the lid chamber side. Are in close contact with each other, and the flange portion of the base plate and the peripheral edge portion of the frame are provided with grooves recessed inward in the radial direction, and the space between the base plate and the lid chamber and the said. It is assumed that the space between the frame and the electric motor communicates with each other through the gap of the groove, and a part of the gap is blocked by the lid chamber near the upper end of the groove.

According to the present invention, it is possible to provide a highly reliable scroll compressor or the like with a simple configuration.

It is a vertical sectional view of the scroll compressor which concerns on 1st Embodiment. In the scroll compressor according to the first embodiment, it is a cross-sectional view of the compressor in line X1-X1 of FIG. It is a perspective view of the state in which the closed container and the like of the scroll compressor which concerns on 1st Embodiment are removed. It is a perspective view which includes the crank shaft, the electric motor, and the balance weight of the scroll compressor which concerns on 1st Embodiment. It is a vertical sectional view which shows the flow of the refrigerant and the like in the scroll compressor which concerns on 1st Embodiment. It is a partially enlarged view of the region S1 shown in FIG. 5A. It is a perspective view of the oil ring provided in the scroll compressor which concerns on 1st Embodiment. FIG. 3 is a cross-sectional view of the scroll compressor according to the first embodiment when the compressor is cut by the X2-X2 line of FIG. It is sectional drawing which shows the positional relationship between the refrigerant flow path of a compression mechanism part, and the notch of an oil ring in the scroll compressor which concerns on 1st Embodiment. It is a vertical sectional view of the scroll compressor which concerns on 2nd Embodiment. It is a vertical sectional view which shows the flow of the refrigerant and the like in the scroll compressor which concerns on 2nd Embodiment. It is a partially enlarged view of the region S2 shown in FIG. 10A. It is a block diagram of the refrigerant circuit of the air conditioner which concerns on 3rd Embodiment. It is a perspective view of the oil ring provided in the scroll compressor which concerns on 1st modification. It is a perspective view of the oil ring provided in the scroll compressor which concerns on the 2nd modification. It is a perspective view of the oil ring provided in the scroll compressor which concerns on 3rd modification. FIG. 3 is a cross-sectional view showing a positional relationship between a refrigerant flow path of a compression mechanism and a notch of an oil ring in a scroll compressor according to a third modification. It is a perspective view of the scroll compressor which concerns on the comparative example which does not have an oil ring, in the state which the closed container and the like are removed.

<< First Embodiment >>
<Structure of scroll compressor>
FIG. 1 is a vertical sectional view of the 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 closed container 1, a compression mechanism unit 2, a crank shaft 3 (drive shaft), a main bearing 4, a swivel bearing 5, an electric motor 6, and an old dam ring 7. And balun weights 8 and 9. Further, the scroll compressor 100 includes a subframe 10, an auxiliary bearing 11, a refueling pump 12, and an oil ring 13 (bulkhead) in addition to the above-described configuration.

The closed container 1 is a shell-shaped container that houses the compression mechanism portion 2, the crank shaft 3, the electric motor 6, the oil ring 13, and the like, and is substantially sealed. Lubricating oil for improving the lubricity of the scroll compressor 100 is sealed in the closed container 1, and is stored as an oil sump R at the bottom of the closed container 1. The closed container 1 includes a cylindrical tubular chamber 1a, a lid chamber 1b that closes the upper side of the tubular chamber 1a, and a bottom chamber 1c that closes the lower side of the tubular chamber 1a. The lid chamber 1b has an inverted U shape in a vertical cross-sectional view. On the other hand, the bottom chamber 1c has a U-shape in a vertical cross-sectional view.

A lid chamber 1b is fixed to the upper end of the cylinder chamber 1a by welding (or press fitting). The outer peripheral surface near the lower end of the lid chamber 1b is in close contact with the inner peripheral surface near the upper end of the tubular chamber 1a. The above-mentioned "adhesion" includes a case where the lid chamber 1b is welded to the tubular chamber 1a and the metal at the welded portion is melted and integrated. Such a configuration in which the lid chamber 1b is fixed to the inside of the tubular chamber 1a is referred to as an "inner cover specification".

As shown in FIG. 1, a suction pipe Pa is inserted and fixed in the lid chamber 1b of the closed container 1. The suction pipe Pa is a pipe that guides the refrigerant to the suction chamber H of the compression mechanism unit 2. Further, a discharge pipe Pb is inserted and fixed (installed) in the cylinder chamber 1a of the closed container 1. The discharge pipe Pb is a pipe that guides the refrigerant compressed by the compression mechanism unit 2 to the outside of the scroll compressor 100. The upstream end e1 (one end) of the discharge pipe Pb is located inside the closed container 1, and the downstream end e2 (the other end) is located outside the closed container 1.

The compression mechanism unit 2 is a mechanism that compresses the refrigerant as the crank shaft 3 rotates. The compression mechanism unit 2 includes a fixed scroll 21, a swivel scroll 22, and a frame 23, and is arranged in the upper space inside the closed container 1.
The fixed scroll 21 is a fixing member fixed in the closed container 1. The fixed scroll 21 has a base plate 21a fixed to the tubular chamber 1a and a spiral fixing wrap 21b.

The base plate 21a includes a thick main body portion 211a that has a circular shape in a plan view, and a flange portion 212a that protrudes radially outward from the lower portion of the main body portion 211a. In order to secure a region Sa (a circular region in the bottom view) in which the swivel lap 22b swivels with respect to the fixed lap 21b, the vicinity of the center of the lower surface of the main body portion 211a is recessed upward in a predetermined manner. Further, a suction chamber H in which the refrigerant is guided via the suction pipe Pa is provided at a predetermined position in the main body 22a.

The fixed wrap 21b has a spiral shape (see also FIG. 2) and extends downward from the base plate 21a in the above-mentioned region Sa. The lower surface of the base plate 21a and the lower end of the fixed wrap 21b are substantially flush with each other.

Further, in the example of FIG. 1, the lower end of the lid chamber 1b is in contact with the flange portion 212a of the base plate 21a. As a result, the movement of the fixed scroll 21 in the vertical direction can be restricted, and a bolt (not shown) for fastening the fixed scroll 21 to the compression mechanism portion 2 becomes unnecessary, so that the configuration of the compression mechanism portion 2 can be simplified. , The scroll compressor 100 can be made compact.

The swivel scroll 22 is a moving member that forms a compression chamber C together with the fixed scroll 21 by swiveling (moving). The swivel scroll 22 includes a disk-shaped end plate 22a, a spiral swirl lap 22b (see also FIG. 2) erected on the end plate 22a, and a boss portion 22c fitted to the upper end of the crank shaft 3. , Is equipped. As shown in FIG. 1, the swivel lap 22b extends above the end plate 22a, while the boss portion 22c extends below the end plate 22a.

FIG. 2 is a cross-sectional view of the scroll compressor 100 in the X1-X1 line of FIG.
As shown in FIG. 2, the spiral fixed lap 21b and the spiral swirl lap 22b mesh with each other to form a compression chamber C between the fixed lap 21b and the swirl lap 22b. The compression chamber C described above is a space for compressing the gaseous refrigerant, and is formed on the outer line side and the inner line side of the swirl lap 22b, respectively. Further, near the center of the base plate 21a of the fixed scroll 21, a discharge port V for guiding the refrigerant compressed in the compression chamber C to the upper space in the closed container 1 is provided. Then, the refrigerant compressed by the compression mechanism unit 2 is discharged toward the ceiling surface of the closed container 1 through the discharge port V (see also FIG. 5A).

The frame 23 shown in FIG. 1 is a member that supports the swivel scroll 22. The frame 23 has a substantially rotationally symmetric shape and is provided under the swivel scroll 22. The frame 23 is provided with a back pressure chamber B in addition to a hole through which the crank shaft 3 is inserted (reference numeral is not shown). The back pressure chamber B is a space having a predetermined intermediate pressure between the suction pressure and the discharge pressure, and is provided on the back surface side of the swivel scroll 22.

The frame 23 includes a relatively thick peripheral edge portion 23a. The peripheral edge portion 23a is a portion of the frame 23 that is radially outer of the end plate 22a of the swivel scroll 22. As shown in FIG. 1, the upper surface of the peripheral edge portion 23a is in contact with the flange portion 212a of the base plate 21a of the fixed scroll 21.

The frame 23 is fixed to the closed container 1 by press fitting or the like. The flange portion 212a of the base plate 21a and the peripheral edge portion 23a of the frame 23 are sandwiched between the cylinder chamber 1a and the lid chamber 1b. Such an installation method is called a press-fit method.

In the example of FIG. 1, the inner peripheral surface of the tubular chamber 1a is substantially flush with each other, and no step (not shown) is particularly provided on the inner peripheral surface. The frame 23 and the fixed scroll 21 are fixed to the tubular chamber 1a, and the lid chamber 1b is in contact with the flange portion 212a of the fixed scroll 21. That is, the peripheral end surface Q1 (see FIG. 5A) of the lid chamber 1b is in close contact with the surface of the flange portion 212a of the base plate 21a on the lid chamber 1b side. Such a configuration is also included in the matter that the flange portion 212a and the peripheral edge portion 23a are sandwiched between the cylinder chamber 1a and the lid chamber 1b (that is, the press-fit method). In addition, "close" means that they are in close contact with each other.

As a configuration different from that of FIG. 1, a predetermined step portion (not shown) is provided on the upper portion of the tubular chamber 1a, while another step portion (not shown) corresponding to the predetermined step portion is provided on the peripheral edge portion 23a of the frame 23. It may be provided. Then, the stepped portion of the frame 23 may be locked by the stepped portion of the tubular chamber 1a. Such a configuration is also included in the above-mentioned press-fit method.

FIG. 3 is a perspective view of the scroll compressor 100 with the closed container 1 and the like removed.
The white arrows in FIG. 3 indicate the flow of mist-like lubricating oil. Further, the arrow on the lower side of the crank shaft 3 in FIG. 3 indicates the direction in which the crank shaft 3 rotates. In the example of FIG. 3, two grooves M for communicating the upper side (one side) and the lower side (the other side) of the compression mechanism portion 2 in the axial direction are provided in the compression mechanism portion 2 (see also FIG. 2). ).

More specifically, the flange portion 212a of the base plate 21a of the fixed scroll 21 is provided with a groove Ma whose outer peripheral wall is recessed inward in the radial direction in parallel with the axial direction of the crank shaft 3. Further, the peripheral edge portion 23a of the frame 23 is provided with a groove Mb in which the outer peripheral wall thereof is recessed inward in the radial direction in parallel with the axial direction of the crank shaft 3. These grooves Ma and Mb are provided so as to have substantially the same circumferential range and are sequentially arranged in the axial direction. Further, the space Su between the base plate 21a and the lid chamber 1b (see FIG. 1) and the motor chamber Sm which is the space between the frame 23 and the motor 6 (see FIG. 1) have a gap u in the groove M. Communicate through. In the example of FIG. 3, such a gap u is provided on the outside of the compression mechanism portion 2.

This gap u is a flow path that guides the refrigerant or the like discharged into the space Su above the compression mechanism unit 2 through the discharge port V to the lower side of the compression mechanism unit 2. In addition to the refrigerant, mist-like lubricating oil is also mixed in the gas flowing through the gap u. Such a gas is called a "refrigerant or the like". Then, the refrigerant or the like discharged to the space Su above the compression mechanism unit 2 via the discharge port V is guided to the motor chamber Sm below the compression mechanism unit 2 via the grooves Ma and Mb in sequence. It has become like.

More specifically, the refrigerant or the like flows through the gap u between the wall surface of the groove Ma of the fixed scroll 21 and the inner peripheral surface of the cylinder chamber 1a (see FIG. 2), and further, the groove Mb of the frame 23 and the groove Mb of the frame 23. The refrigerant or the like passes through the gap u between the inner peripheral surface of the tubular chamber 1a (see FIG. 2) and the inner peripheral surface. Therefore, in the closed container 1, the space Su on the upper side of the compression mechanism unit 2 and the motor chamber Sm on the lower side of the frame 23 are predetermined discharge pressure spaces whose pressures are substantially equal to the discharge pressure of the refrigerant.

As shown in FIG. 2, it is preferable that the two grooves M are unevenly distributed on the side opposite to the discharge pipe Pb in the circumferential direction. For example, a straight line passing through the insertion position of the discharge pipe Pb and the central axis Y of the crank shaft 3 and perpendicular to the central axis Y is defined as a straight line L1. Further, a straight line that intersects both the straight line L1 and the central axis Y of the crank shaft 3 perpendicularly is defined as a straight line L2.

Then, two grooves M may be provided (unevenly distributed) on the side opposite to the discharge pipe Pb with the straight line L2 as a reference. As a result, the length in the circumferential direction from the groove M to the discharge pipe Pb is sufficiently secured in the cross-sectional view. Therefore, it is possible to prevent the mist-like lubricating oil that descends from the gap u from flowing out through the discharge pipe Pb.

Returning to FIG. 1 again, the explanation will be continued.
The crank shaft 3 is a shaft that rotates integrally with the rotor 6b of the motor 6, and extends in the vertical direction. As shown in FIG. 1, the crank shaft 3 includes a main shaft 3a and an eccentric portion 3b extending upward from the main shaft 3a.

The spindle 3a is coaxially fixed to the rotor 6b of the motor 6 and rotates integrally with the rotor 6b. The eccentric portion 3b is an axis that rotates while being eccentric with respect to the main shaft 3a, and is fitted to the boss portion 22c of the swivel scroll 22 described above. Then, the eccentric portion 3b rotates while being eccentric, so that the swivel scroll 22 turns.

The main bearing 4 rotatably supports the upper portion of the main shaft 3a with respect to the frame 23, and is fixed to the peripheral wall surface of the hole (reference numeral is not shown) of the frame 23.
The swivel bearing 5 rotatably supports the eccentric portion 3b with respect to the boss portion 22c of the swivel scroll 22, and is fixed to the inner peripheral wall of the boss portion 22c.

It is preferable that the main bearing 4 and the swivel bearing 5 are composed of a slide bearing (journal bearing). That is, it is preferable that the plurality of bearings (main bearing 4 and swivel bearing 5) that pivotally support the crank shaft 3 in the frame 23 are composed of only slide bearings. According to such a configuration, the inner peripheral surface of the main bearing 4 and the swivel bearing 5 and the outer peripheral surface of the crank shaft 3 are in surface contact with each other, so that a large load is applied to the main bearing 4 and the swivel bearing 5 during high-speed rotation. However, the vibration of the crank shaft 3 is suppressed. Further, as compared with the case where bearings of other types other than the sliding bearings are used as the main bearing 4 and the swivel bearing 5, the configuration can be simplified and the cost can be reduced.

Further, the crank shaft 3 has a through hole 3c for guiding the lubricating oil. The lubricating oil flowing through the through hole 3c is guided to the main bearing 4, the swivel bearing 5, the auxiliary bearing 11, and the like in addition to the compression mechanism portion 2.

The electric motor 6 is a drive source for rotating the crank shaft 3, and is installed inside the closed container 1. In the example of FIG. 1, the electric motor 6 is installed between the oil ring 13 and the subframe 10 in the vertical direction. The electric motor 6 includes a stator 6a and a rotor 6b. The stator 6a is fixed to the inner peripheral wall of the tubular chamber 1a by press fitting or the like. The rotor 6b is rotatably arranged inside the stator 6a in the radial direction.

The old dam ring 7 is a ring-shaped member that receives the eccentric rotation of the eccentric portion 3b and rotates the swivel scroll 22 without rotating. The old dam ring 7 is provided between the swivel scroll 22 and the frame 23.
The balance weights 8 and 9 are members for suppressing the vibration of the scroll compressor 100. On the other hand, the balun weight 8 is provided inside the oil ring 13 in the radial direction. More specifically, the balance weight 8 is provided inside the oil ring 13 (partition wall) in the radial direction in the motor chamber Sm. The other balun weight 9 has an arc shape and is fixed to the lower surface of the rotor with rivets 9a.

FIG. 4 is a perspective view including a crank shaft 3, an electric motor 6, and a balance weight 8.
The arrow on the lower side of the crank shaft 3 in FIG. 4 indicates the direction in which the crank shaft 3 rotates. As shown in FIG. 4, the balance weight 8 includes an annular portion 8a having an annular shape and an arc portion 8b having an arc shape.

Then, the annular portion 8a is fixed to the crank shaft 3 in a state where the crank shaft 3 is inserted into the hole (the reference numeral is not shown) of the annular portion 8a. The arcuate portion 8b has an arcuate shape in a cross-sectional view so as to surround a half circumference of the crank shaft 3, and extends upward in the axial direction from the annular portion 8a. Then, as the electric motor 6 is driven, the balance weight 8 rotates integrally with the crank shaft 3.

The subframe 10 shown in FIG. 1 rotatably supports the lower portion of the crank shaft 3 and is fixed to the inner peripheral wall of the closed container 1. The subframe 10 is provided with a hole (not shown) through which the crank shaft 3 is inserted, and the auxiliary bearing 11 is fixed to the peripheral wall surface of the hole.
The auxiliary bearing 11 is a bearing that supports the lower portion of the crank shaft 3 and receives a radial load from the crank shaft 3. The auxiliary bearing 11 is fixed to the peripheral wall surface of the hole (not shown by reference numeral) of the subframe 10 by press fitting or the like.

The lubrication pump 12 is a non-volumetric pump that pumps lubricating oil, and is provided in the lower part of the through hole 3c. In the example of FIG. 1, the refueling pump 12 includes a thin plate-shaped metal piece 12a. Then, the lubricating oil rises through the through hole 3c due to the rotation of the metal piece 12a accompanying the drive of the electric motor 6.

The oil ring 13 is a tubular "partition wall" that separates the upstream end e1 (one end) of the discharge pipe Pb and the cylindrical chamber 1a, and is provided between the compression mechanism portion 2 and the electric motor 6. As shown in FIG. 1, the oil ring 13 is fixed (installed) to the frame 23 of the compression mechanism unit 2 in a state of being in contact with the frame 23.

FIG. 5A is a vertical sectional view showing the flow of the refrigerant and the like in the scroll compressor 100.
The white arrow in FIG. 5A indicates the flow of the refrigerant or the like. Further, FIG. 5A shows a vertical cross section when the scroll compressor 100 is cut on a predetermined plane (not shown) including the groove M, and the cut surface in the vertical cross-sectional view is different from that of FIG.

As shown in FIG. 5A, the refrigerant and the like (including mist-like lubricating oil) discharged into the space Su above the compression mechanism portion 2 via the discharge port V are present on the wall surface of the groove M and the inner circumference of the cylinder chamber 1a. It descends through the gap u between the surfaces. Then, the refrigerant or the like flowing out from the gap u descends through the annular gap k between the oil ring 13 and the cylinder chamber 1a, which will be described later.

FIG. 5B is a partially enlarged view of the region S1 shown in FIG. 5A.
As shown in FIG. 5B, in the vicinity of the upper end of the groove M provided in the compression mechanism portion 2, a part of the gap u between the wall surface of the groove M and the inner peripheral surface of the cylinder chamber 1a is blocked by the lid chamber 1b. Has been done. In other words, at the lower end of the lid chamber 1b, a portion corresponding to the gap u in the circumferential direction faces the gap u. Therefore, since the cross-sectional area of the flow path of the gap u becomes narrow near the upper end of the groove M, the flow velocity of the mist-like lubricating oil increases in the process of flowing through the gap u.

FIG. 15 is a perspective view of a scroll compressor 100D according to a comparative example not provided with an oil ring, in a state where the closed container 1 and the like are removed.
The white arrows in FIG. 15 indicate the flow of mist-like lubricating oil. Further, the arrow on the lower side of the crank shaft 3 in FIG. 15 indicates the direction in which the crank shaft 3 rotates. In the press-fit type scroll compressor 100D, as described above, the flow velocity of the refrigerant or the like increases in the process of passing through the gap M of the groove M of the compression mechanism unit 2. Then, as shown by the white arrow in FIG. 15, the refrigerant or the like that has flowed out (scattered) to the lower side of the compression mechanism portion 2 is entrained in the swirling flow due to the rotation of the balance weight 8, and thus is lubricated via the discharge pipe Pb. Oil is likely to flow out. Therefore, in the first embodiment, the oil ring 13 (see FIG. 1) is provided to suppress the outflow of the lubricating oil through the discharge pipe Pb.

FIG. 6 is a perspective view of the oil ring 13 included in the scroll compressor 100.
As shown in FIG. 6, the oil ring 13 includes a cylindrical portion 13a having a thin cylindrical shape, and an annular fixing portion 13b extending radially inward from the upper end of the cylindrical portion 13a.
The fixing portion 13b is a portion fixed to the frame 23 (see FIG. 1). In the example of FIG. 6, three holes h are provided in the fixed portion 13b at intervals of about 120 ° in the circumferential direction. Then, a screw (not shown) is inserted into each hole h, and further screwed into a screw hole (not shown) provided on the lower surface of the frame 23.

As a result, the upper surface of the oil ring 13 comes into close contact with the lower surface of the frame 23 (see FIG. 1) over the entire circumference in the circumferential direction. Therefore, there is almost no gap between the oil ring 13 and the frame 23. The upstream end e1 of the discharge pipe Pb (see FIG. 1) is provided between the radial inner end of the fixed portion 13b and the radial outer end of the fixed portion 13b in a plan view. It is preferable to have. In other words, in a plan view, it is preferable that the upstream end e1 of the discharge pipe Pb overlaps the fixed portion 13b. According to such a configuration, the lubricating oil via the discharge pipe Pb is compared with the configuration in which the upstream end e1 of the discharge pipe Pb penetrates further in the radial direction than the radial inner end of the fixed portion 13b. Outflow can be suppressed. For example, even if oil droplet-shaped lubricating oil is accumulated on the balance weight 8, since the distance to the upstream end e1 of the discharge pipe Pb is relatively long, the outflow of the lubricating oil through the discharge pipe Pb can be suppressed.

The cylindrical portion 13a shown in FIG. 6 has a function of separating the upstream end e1 of the discharge pipe Pb (see FIG. 1) and the cylinder chamber 1a. Here, the cylindrical portion 13a "separates" the upstream end e1 of the discharge pipe Pb from the cylinder chamber 1a means that the lubricating oil flowing out into the cylinder chamber 1a through the gap u is directly guided to the discharge pipe Pb. However, it means that it is temporarily blocked by the cylindrical portion 13a. Even if the flow of the lubricating oil from the gap u to the discharge pipe Pb is not completely blocked, if this flow is suppressed, it is included in the above-mentioned meaning of "separate".

As shown in FIG. 1, a radial gap k is provided over the entire circumference of the cylindrical portion 13a between the outer peripheral surface of the cylindrical portion 13a and the inner peripheral surface of the closed container 1. Then, the refrigerant or the like that has descended through the gap u of the compression mechanism portion 2 swirls and descends through the annular gap k between the cylindrical portion 13a and the closed container 1. That is, the cylindrical portion 13a of the oil ring 13 has a function of suppressing the outflow of the lubricating oil from the discharge pipe Pb and also having a function of guiding the flow of the refrigerant or the like.

As shown in FIG. 5B, the distance L4 between the wall surface of the groove M and the cylinder chamber 1a is longer than the distance L3 between the lower end of the lid chamber 1b and the flange portion 212a of the base plate 21a. preferable. Further, as shown in FIG. 5A, it is preferable that the distance L5 between the cylinder chamber 1a and the oil ring 13 is longer than the distance L4 between the wall surface of the groove M and the cylinder chamber 1a. According to such a configuration, even if the flow velocity of the refrigerant or the like increases once in the process of entering the gap u of the groove M, the annular gap k on the radial outer side of the oil ring 13 is relatively large. The flow velocity of the refrigerant or the like decreases in the process of passing. As a result, the mist-like oil and the refrigerant gas are separated in the process of descending while swirling the annular gap k, so that the outflow of the lubricating oil through the discharge pipe Pb can be suppressed.
When the wall surface of the groove M has a predetermined unevenness (not shown), the above-mentioned distance L4 is a value obtained by averaging the distance between the wall surface of the groove M and the cylinder chamber 1a at a plurality of points in the axial direction. do.

Further, the diameter of the outer peripheral surface of the cylindrical portion 13a is equal to or less than the diameter of the bottom of the groove M (see FIG. 3) forming the gap u with reference to the central axis Y of the crank shaft 3 (see FIG. 1). Is preferable. According to such a configuration, the fixing portion 13b (see FIG. 6) of the oil ring 13 is hidden inside the groove M in the radial direction. Therefore, it is possible to prevent the flow of the refrigerant or the like descending through the gap u from being obstructed by the fixed portion 13b of the oil ring 13.

As shown in FIG. 6, the oil ring 13 is provided with three notches s1, s2, s3. A discharge pipe Pb (see FIG. 1) is inserted through the first notch s1 (first insertion portion, discharge pipe insertion portion). A power supply terminal E (also referred to as a hermetic terminal: see FIG. 2) is inserted through the second notch s2 (second insertion portion). The power supply terminal E is a terminal connected to the winding 61b (see FIG. 1) of the motor 6. Then, the oil return pipe 15 (see FIG. 7) is inserted into the third notch s3 (third insertion portion). The oil return pipe 15 is a pipe that guides a part of the lubricating oil contained in the refrigerant or the like of the compression mechanism unit 2 (see FIG. 1) to the oil sump R of the closed container 1.

FIG. 7 is a cross-sectional view when the scroll compressor 100 is cut along the line X2-X2 of FIG.
In addition, when the scroll compressor 100 is cut by the X2-X2 line of FIG. 1, the discharge pipe Pb and the power supply terminal E which are not actually seen are projected and shown in FIG. 7 for explanation. Further, FIG. 7 illustrates four legs 14 installed in the bottom chamber 1c of the closed container 1 (see FIG. 1).

As shown in FIG. 7, the stator 6a of the electric motor 6 includes a core back 61a in which electromagnetic steel sheets are laminated, and a winding 61b that is predeterminedly wound around the core back 61a. In the core back 61a of the stator 6a, a plurality of oil flow paths N (first flow path: the figure) that allow the upper side (one side) and the lower side (the other side) of the stator 6a to communicate with each other in the axial direction of the crank shaft 3. 3) is provided. In addition to the mist-like lubricating oil, the gaseous refrigerant and the like flowing through the "oil flow path N" are also mixed.

The oil flow path N described above is a flow path that guides a refrigerant or the like passing through an annular gap k (see FIG. 1) between the oil ring 13 and the closed container 1 to the lower side of the motor 6. That is, on the outer peripheral wall of the core back 61a of the stator 6a, a groove in which a predetermined portion in the circumferential direction is recessed inward in the radial direction is provided in the vertical direction as an oil flow path N.

In the example of FIG. 7, in the core back 61a of the stator 6a, six oil flow paths N are provided at substantially equal intervals in the circumferential direction. Then, the refrigerant or the like is guided to the lower side of the motor 6 through the gap between the groove (oil flow path N) of the core back 61a and the inner peripheral surface of the closed container 1.

The cross-sectional area of the flow path of the gap u at the upper end of the groove M (see FIG. 5B) is preferably smaller than the cross-sectional area of the flow path of the oil flow path N (first flow path: see FIG. 7). Here, the "gap u at the upper end of the groove M" means a narrow gap between the upper end of the groove M (see FIG. 5B) and the lower end of the lid chamber 1b. According to such a configuration, even if the flow velocity of the refrigerant or the like increases in the process of entering the gap u from the space Su (see FIG. 5A) on the upper side of the compression mechanism portion 2, the oil flow having a relatively large flow path cross-sectional area. In the process of passing through the passage N, the flow velocity of the refrigerant or the like becomes small, and the lubricating oil is easily separated from the refrigerant or the like.

Further, it is preferable that the oil ring 13 is provided on the inner side in the radial direction of each oil flow path N in the cross-sectional view. According to such a configuration, the refrigerant or the like passing through the annular gap k (see FIG. 1) between the oil ring 13 and the closed container 1 passes through the oil flow path N of the core back 61a and the electric motor 6 It is guided to the lower side as it is. Further, even when the mist-like lubricating oil is blown up through the oil flow path N, it is possible to prevent the lubricating oil from entering the inside of the oil ring 13.

Further, in a cross-sectional view including the notches s1, s2, s3 (where the discharge pipe Pb is inserted into the notch s1 of the oil ring 13) shown in FIG. 7, at least a part of the six oil flow paths N. However, it is preferable that the oil ring 13 overlaps the oil ring 13 in the radial direction. The "cross section" in the cross section is a plane perpendicular to the central axis Y (see FIG. 1) of the crank shaft 3.

As a specific example, in the cross-sectional view including the notches s1, s2, s3, 60% or more of the total value of the circumferential lengths of the six oil flow paths N overlaps the oil ring 13 in the radial direction. Is preferable. According to such a configuration, the lubricating oil that descends while swirling through the annular gap k (see FIG. 1) between the oil ring 13 and the closed container 1 fills the gaps of the notches s1, s3, and s3. It is possible to prevent the oil ring 13 from entering the inside through the oil ring 13.

Further, it is preferable that the oil ring 13 is provided on the radial outer side of the winding 61b of the electric motor 6 in the cross-sectional view. According to such a configuration, when the gaseous refrigerant guided to the lower side of the motor 6 is guided to the space inside the oil ring 13 through the gap of the winding 61b or the like, the oil ring 13 and the closed container are used. It becomes difficult to enter the gap k (see FIG. 1) between 1 and 1. Then, after the refrigerant or the like moves to the lower side of the motor 6, the mist-like lubricating oil is integrated into the oil sump R, while the gaseous refrigerant blows up inside the oil ring 13 to form a circulating flow. Lubricate.

Next, the positional relationship between the oil ring 13 and the balance weight 8 will be described.
As shown in FIG. 1, it is preferable that the upstream end e1 (one end) of the discharge pipe Pb is located between the upper surface and the lower surface of the balance weight 8 in the axial direction of the crank shaft 3. According to such a configuration, even if the lubricating oil dripping from the balance weight 8 and accumulated on the upper surface of the electric motor 6 becomes mist again, the upstream end e1 of the discharge pipe Pb is above the lower surface of the balance weight 8. Since it is located, the outflow of lubricating oil through the discharge pipe Pb can be suppressed. Further, even when the lubricating oil accumulated on the upper surface of the annular portion 8a (see FIG. 4) of the balance weight 8 is misted again and blown upward, the upstream end e1 of the discharge pipe Pb is from the upper surface of the balance weight 8. Is located on the lower side, so that the outflow of lubricating oil through the discharge pipe Pb can be suppressed.

Further, as shown in FIG. 1, it is preferable that a predetermined space D is provided between the electric motor 6 and the oil ring 13 in the axial direction. More specifically, it is preferable that a predetermined space D is provided between the upper surface of the core back 61a of the electric motor 6 and the lower end of the oil ring 13. As a result, a predetermined insulation distance can be secured between the metal oil ring 13 and the electric motor 6. Further, by making the oil ring 13 made of metal, the strength of the oil ring 13 becomes higher than that of the case made of resin. Therefore, even in a configuration in which the three notches s1, s2, and s3 are provided, deformation and breakage of the oil ring 13 can be suppressed.

Further, the distance L1 between the upper surface of the balance weight 8 and the lower surface of the peripheral edge portion 23a of the frame 23 is from the distance L2 between the lower surface of the balance weight 8 and the upper surface of the core back 61a of the stator 6a. Is also preferred to be short. According to such a configuration, since the vertical distance L2 between the balun weight 8 and the electric motor 6 is relatively long, even if the lubricating oil accumulated on the upper surface of the electric motor 6 becomes mist again, the balun weight 8 is used. The oil droplet formation of the lubricating oil in the above is suppressed. Therefore, the outflow of the lubricating oil through the discharge pipe Pb can be suppressed.

As described above, the oil ring 13 shown in FIG. 6 is provided with three notches s1, s2, and s3. A discharge pipe Pb (see FIG. 1) is inserted through the first notch s1 (first insertion portion, discharge pipe insertion portion). The notch s1 is provided in the vertical direction from the vicinity of the middle in the height direction to the lower end of the oil ring 13 in the oil ring 13, and is opened at the lower end (motor 6 side) of the oil ring 13.

Further, as shown in FIG. 1, the upstream end e1 of the discharge pipe Pb is located inside the oil ring 13 in the radial direction. In other words, the upstream end e1 of the discharge pipe Pb faces the inside of the oil ring 13. As a result, it is possible to prevent the lubricating oil flowing through the annular gap k between the oil ring 13 and the closed container 1 from flowing out through the discharge pipe Pb.

Further, as described above, the notch s1 is provided in the lower part of the oil ring 13 (the lower part of the oil ring 13 is notched). As a result, a sufficient vertical length between the upper surface of the oil ring 13 and the notch s1 can be secured as compared with the configuration in which the notch (not shown) is provided on the upper portion of the oil ring 13.

Further, since the position of the notch s1 is the lower part of the oil ring 13, the ratio of the circumferential component (swivel component) in the velocity vector of the refrigerant or the like flowing through the annular gap k can be reduced. can. As a result, a flow in which the refrigerant or the like descends while appropriately swirling through the annular gap k is likely to occur. Further, since a sufficient vertical length between the upper surface of the oil ring 13 and the notch s1 can be sufficiently secured, mist-like lubrication that descends while swirling through an annular gap k (see FIG. 1). Before the oil reaches the notch s1, it becomes easy to form oil droplets on the outer peripheral surface of the oil ring 13 and the inner wall surface of the closed container 1.

As shown in FIG. 6, in the configuration in which the notch s1 is open to the lower side of the oil ring 13 (the notch s1 is provided at the lower end of the oil ring 13), the notch s1 is the oil ring. It is included in the matter that it is provided in the "lower part" of 13.

The second notch s2 (second insertion portion) shown in FIG. 6 is a notch for inserting the power supply terminal E (see FIG. 2) and routing the power cable (not shown). The notch s2 includes a terminal insertion portion sa2 into which the power supply terminal E is inserted, and a wide portion sb2 for routing a power cable (not shown). The terminal insertion portion sa2 is provided in the vertical direction from a predetermined position in the height direction of the oil ring 13 to the lower end of the oil ring 13, and is opened at the lower end of the oil ring 13.

The wide portion sb2 is provided over a predetermined range in the circumferential direction from the lower portion of the terminal insertion portion sa2, and is opened at the lower end of the oil ring 13. That is, a wide portion sb2 is provided on the downstream side of the terminal insertion portion sa2 in the circumferential direction with reference to the direction in which the crank shaft 3 rotates (not shown in FIG. 6, see FIG. 3).

An oil return pipe 15 (see FIG. 7) is inserted through the third notch s3 (third insertion portion). The notch s3 is provided in the oil ring 13 in a vertically elongated shape from the vicinity of the upper portion in the height direction to the lower end of the oil ring 13, and is opened at the lower end of the oil ring 13.

FIG. 8 is a cross-sectional view showing the positional relationship between the gap u of the compression mechanism portion and the notches s1, s2, s3 of the oil ring 13.
In FIG. 8, the electric motor 6 and the like are omitted in the cross section (the same cross section as in FIG. 7) when the scroll compressor 100 is cut by the X2-X2 line of FIG. Further, when the scroll compressor 100 is cut by the X2-X2 line of FIG. 1, the gap u, the discharge pipe Pb, and the power supply terminal E, which are not actually visible, are projected in FIG. 8 for explanation. Shows.
Further, the position X3 in FIG. 8 indicating the position in the circumferential direction corresponds to the position X3 in FIG. 7. Further, the right-handed arrow on the paper shown in FIG. 8 indicates the direction in which the crank shaft 3 rotates.

As shown in FIG. 8, two oil rings 13 are provided on a virtual plane T including the central axis Y of the crank shaft 3 and including the end point m on the upstream side of the gap u with reference to the direction in which the crank shaft 3 rotates. When divided, it is preferable that the following relationship holds. That is, when the oil ring 13 is divided into two by the virtual plane T described above, in the oil ring 13, the side area of one side A1 on the gap u side (the side opposite to the discharge pipe Pb) is the other side A2. It is preferably larger than the side area.

From another point of view, it is preferable that at least a part of the notch s2 through which the power supply terminal E is inserted and the notch s1 through which the discharge pipe Pb is inserted are provided on the other side A2 described above. Further, it is preferable that the positions of the two gaps u in the circumferential direction are unevenly distributed on the side opposite to the discharge pipe Pb. According to such a configuration, the refrigerant or the like that has exited the gap u first passes through the gap k (see FIG. 1) between one side A1 of the oil ring 13 and the closed container 1 and is on the right side of the paper in FIG. It descends while turning around.

Here, since the one side A1 of the oil ring 13 has a larger side area than the other side A2 (that is, the gap through which the lubricating oil enters is narrow), the lubricating oil contained in the refrigerant or the like can be transferred from the one side A1 to the oil ring 13. It becomes difficult to get inside. Then, most of the lubricating oil discharged from the gap u reaches the motor 6 while flowing through one side A1 of the oil ring 13, and is further guided to the lower side of the motor 6 via the oil flow path N.

Further, the arrangement of the gap u, the discharge pipe Pb, and the power supply terminal E in the circumferential direction is preferably in the order of the gap u, the discharge pipe Pb, and the power supply terminal E with respect to the direction in which the crank shaft 3 rotates. According to such a configuration, a sufficient length in the circumferential direction from the gap u to the notch s2 for the power supply terminal E can be sufficiently secured. Therefore, the mist-like lubricating oil that descends while swirling through the gap k (see FIG. 1) between the oil ring 13 and the closed container 1 reaches the oil flow path N (FIG. 3) before reaching the notch s2. , See FIG. 7) and guided to the underside of the motor 6. As a result, it is possible to prevent the mist-like lubricating oil from entering the inside of the oil ring 13.

<Effect>
According to the first embodiment, the flange portion 212a of the base plate 21a and the peripheral edge portion 23a of the frame 23 are sandwiched between the cylinder chamber 1a and the lid chamber 1b. By adopting such a press-fitting configuration, the configuration of the scroll compressor 100 can be simplified.

Further, the upstream end e1 of the discharge pipe Pb and the cylinder chamber 1a are separated by an oil ring 13. That is, the region where the rotating body such as the crank shaft 3 and the balun weight 8 is provided and the gap k into which the refrigerant or the like descends are partitioned by the oil ring 13. Therefore, even if the flow velocity of the refrigerant or the like increases in the process of entering the gap u from the space Su on the upper side of the compression mechanism portion 2, the refrigerant or the like is hardly agitated by the rotation of the crank shaft 3 or the balun weight 8. Then, the flow velocity of the refrigerant or the like gradually decreases in the process of flowing through the annular gap k, and the refrigerant or the like reaches the motor 6 through the gap k by a linear path. This makes it possible to promote the formation of mist-like lubricating oil into oil droplets. In addition, it is possible to prevent the lubricating oil once oil droplets from becoming mist again.

Further, since the upstream end e1 of the discharge pipe Pb is located inside the oil ring 13, the outflow of the lubricating oil through the discharge pipe Pb is suppressed, and by extension, each sliding portion of the scroll compressor 100 is appropriately slid. Can be lubricated. As described above, according to the first embodiment, it is possible to provide a highly reliable scroll compressor 100 with a simple configuration.

<< Second Embodiment >>
The second embodiment is different from the first embodiment in that the lid chamber 1Ab (see FIG. 9) is a "covering specification" in which the lid chamber 1Ab is fixed to the outside of the tubular chamber 1a. The other points are the same as those in the first embodiment. Therefore, the parts different from the first embodiment will be described, and the description of the overlapping parts will be omitted.

FIG. 9 is a vertical sectional view of the scroll compressor 100A according to the second embodiment.
As shown in FIG. 9, the lid chamber 1Ab is subjected to a predetermined bending process so that the lower end portion thereof is enlarged in diameter. The inner peripheral surface of the lower end of the lid chamber 1Ab is in close contact with the outer peripheral surface of the upper end of the tubular chamber 1a. That is, a part Q2 of the inner wall surface of the lid chamber 1Ab (a portion where the lid chamber 1Ab is bent in a vertical cross-sectional view to form a step) is in close contact with the surface of the flange portion 212a of the base plate 21a on the lid chamber 1Ab side. .. The flange portion 212a of the base plate 21a of the fixed scroll 21 and the peripheral edge portion 23a of the frame 23 are sandwiched between the cylinder chamber 1a and the lid chamber 1b. As described above, the scroll compressor 100A has a press-fit type configuration with an outer cover specification.

FIG. 10A is a vertical cross-sectional view showing the flow of the refrigerant and the like in the scroll compressor 100A.
As shown in FIG. 10A, the refrigerant or the like discharged to the space Su above the compression mechanism unit 2 through the discharge port V descends through the gap u between the wall surface of the groove M and the cylinder chamber 1a. Then, the refrigerant or the like flowing out from the gap u descends through the annular gap k between the oil ring 13 and the cylinder chamber 1a.

10B is a partially enlarged view of the region S2 shown in FIG. 10A.
As shown in FIG. 10B, in the vicinity of the upper end of the groove M provided in the compression mechanism portion 2, a part of the gap u between the wall surface of the groove M and the cylinder chamber 1a is a bent portion of the lid chamber 1b. It is blocked by 1bs. Therefore, since the cross-sectional area of the flow path of the gap u becomes narrow near the upper end of the groove M, the flow velocity of the mist-like lubricating oil increases in the process of flowing through the gap u. Even if the flow velocity of the lubricating oil increases in this way, since the oil ring 13 is provided, the refrigerant or the like is hardly affected by the stirring by the rotating body such as the crank shaft 3 or the balun weight 8, and the refrigerant or the like hardly affects the stirring. Lubricating oil is easily separated.

<Effect>
According to the second embodiment, since the oil ring 13 is provided in the scroll compressor 100A having the outer cover specification, the separation of the lubricating oil from the refrigerant or the like is promoted. Therefore, the configuration of the scroll compressor 100A can be simplified and its reliability can be improved.

<< Third Embodiment >>
In the third embodiment, the air conditioner W (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 block diagram of the refrigerant circuit K of the air conditioner W according to the third embodiment.
The solid line arrow in FIG. 11 indicates the flow of the refrigerant during the heating operation.
On the other hand, the broken line arrow in FIG. 11 indicates the flow of the refrigerant during the cooling operation.
The air conditioner W is a device that performs air conditioning such as cooling and heating. As shown in FIG. 11, the air conditioner W includes a scroll compressor 100, an outdoor heat exchanger Eo, an outdoor fan Fo, an expansion valve Ve, a four-way valve Vf, an indoor heat exchanger Ei, and an indoor fan. It is equipped with Fi.

In the example shown in FIG. 11, the scroll compressor 100, the outdoor heat exchanger Eo, the outdoor fan Fo, the expansion valve Ve, and the four-way valve Vf are provided in the outdoor unit Wo. On the other hand, the indoor heat exchanger Ei and the indoor fan Fi are provided in the indoor unit Wi.

The scroll compressor 100 is a device that compresses a gaseous refrigerant, and has the same configuration as that of the first embodiment (see FIG. 1).
The outdoor heat exchanger Eo is a heat exchanger in which heat is exchanged between the refrigerant passing through the heat transfer tube (not shown) and the outside air sent from the outdoor fan Fo.
The outdoor fan Fo is a fan that sends outside air to the outdoor heat exchanger Eo. The outdoor fan Fo includes an outdoor fan motor Mo which is a drive source, and is installed in the vicinity of the outdoor heat exchanger Eo.

The indoor heat exchanger Ei is a heat exchanger in which heat is exchanged between the refrigerant passing through the heat transfer tube (not shown) and the indoor air (air in the air conditioning target space) sent from the indoor fan Fi. Is.
The indoor fan Fi is a fan that sends indoor air to the indoor heat exchanger Ei. The indoor fan Fi includes an indoor fan motor Mi as a drive source, and is installed in the vicinity of the indoor heat exchanger Ei.

The expansion valve Ve is a valve that reduces the pressure of the refrigerant condensed by the "condenser" (one of the outdoor heat exchanger Eo and the indoor heat exchanger Ei). The refrigerant decompressed by the expansion valve Ve is guided to an "evaporator" (the other of the outdoor heat exchanger Eo and the indoor heat exchanger Ei).

The four-way valve Vf is a valve that switches the flow path of the refrigerant according to the operation mode of the air conditioner W. For example, during cooling operation (see the dashed arrow in FIG. 11), the scroll compressor 100, the outdoor heat exchanger Eo (condenser), the expansion valve Ve, and the indoor heat exchanger Ei (evaporator) are four-way valves. In the refrigerant circuit K sequentially connected via Vf, the refrigerant circulates in the refrigeration cycle.

On the other hand, during the heating operation (see the solid line arrow in FIG. 11), the scroll compressor 100, the indoor heat exchanger Ei (condenser), the expansion valve Ve, and the outdoor heat exchanger Eo (evaporator) are four-way valves. In the refrigerant circuit K sequentially connected via Vf, the refrigerant circulates in the refrigeration cycle.

As described above, in the refrigerant circuit K, the refrigerant circulates sequentially through the scroll compressor 100, the “condenser”, the expansion valve Ve, and the “evaporator”. Devices such as the scroll compressor 100, the outdoor fan Fo, the expansion valve Ve, and the indoor fan Fi are driven based on a command from a control device (not shown).

<Effect>
According to the third embodiment, since the lubricating oil can be suppressed from flowing out from the scroll compressor 100, the reliability and performance of the air conditioner W can be improved.

≪Variation example≫
Although the scroll compressor 100 and the air conditioner W 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 the first embodiment, the configuration in which the oil ring 13 (see FIG. 6) is provided with three notches s1, s2, s3 has been described, but the number of notches is not limited to this and can be appropriately changed. be.

Further, in the first embodiment, the compression mechanism portion 2 is provided with two grooves M (see FIG. 2), and the stator 6a of the motor 6 is provided with six oil flow paths N (first flow paths). As described above, the number of grooves M and oil flow paths N is not limited to this. The same can be said for the second embodiment.

FIG. 12A is a perspective view of the oil ring 13A included in the scroll compressor according to the first modification.
In the first embodiment, the configuration in which the notches s1, s2, and s3 are provided in the oil ring 13 (see FIG. 6) has been described, but the present invention is not limited to this. For example, instead of the notch s1, as shown in FIG. 12A, a hole s11 (first insertion portion, discharge pipe insertion portion) through which the discharge pipe Pb (see FIG. 1) is inserted may be provided. The same applies to the other notches s2 and s3.

Further, it is preferable that the hole s11 (first insertion portion, discharge pipe insertion portion) through which the discharge pipe Pb is inserted is provided in the lower part of the oil ring 13A. As a result, the flow of the refrigerant or the like in the annular gap k (see FIG. 1) is less likely to be adversely affected by the flow of the refrigerant or the like (turbulent flow) inside the oil ring 13A, and the flow of the refrigerant or the like is less likely to be disturbed. .. The fact that the hole s11 is provided in the "lower part" of the oil ring 13A means that the area of the portion of the hole s11 that exists in the lower part of the oil ring 13A is located in the upper part of the oil ring 13A. It means that it is larger than the area of the existing part.

FIG. 12B is a perspective view of the oil ring 13B included in the scroll compressor according to the second modification.
As shown in FIG. 12B, a slit s12 from the upper end to the lower end of the oil ring 13B is provided instead of the notch s1 (see FIG. 6) described in the first embodiment, and the discharge pipe Pb is inserted through the slit s12. You may do so. In addition, a "first insertion section" through which the discharge pipe Pb is inserted, a "second insertion section" through which the power supply terminal E is inserted, and a "third insertion section" through which the oil return pipe 15 (see FIG. 7) is inserted. , Two or three of the notches, holes, and slits may be mixed.

FIG. 13 is a perspective view of the oil ring 13C included in the compressor according to the third modification.
The oil ring 13C shown in FIG. 13 has a configuration in which the notch s3 through which the oil return pipe 15 (see FIG. 7) is inserted is omitted from the oil ring 13 (see FIG. 6) described in the first embodiment. .. In such an oil ring 13C (partition wall), the oil ring 13C is present over the entire circumference in the circumferential direction at least a part above the discharge pipe Pb (see FIG. 1) (above the notch s1). A region G (cylindrical region) is provided. Although the first embodiment also provides a region (not shown in FIG. 6) in which the oil ring 13 (see FIG. 6) exists over the entire circumference in the circumferential direction, a third modification is provided. The vertical width of the region G is longer in the case of.

By providing the above-mentioned region G (see FIG. 13), the oil ring 13C and the closed container 1 (see FIG. 1) descend through an annular gap k (see FIG. 1) while appropriately swirling. Refrigerant flow is likely to occur. Further, in the process of passing through the annular gap k (see FIG. 1), the mist-like lubricating oil is likely to become oil droplets on the outer peripheral surface of the oil ring 13C and the inner wall surface of the closed container 1. Therefore, the outflow of the lubricating oil through the discharge pipe Pb can be suppressed.

FIG. 14 is a cross-sectional view showing the positional relationship between the gap u of the compression mechanism portion and the notches s1 and s2 of the oil ring in the scroll compressor 100C according to the third modification.
Note that FIG. 14 is the same as FIG. 8 except that the oil return pipe 15 (see FIG. 7) and the notch s3 (see FIG. 8) are omitted. The compression mechanism portion 2 shown in FIG. 14 is provided with two gaps u. Further, the discharge pipe is located at a position 90 ° or more away from the end point m2 located on the most downstream side in the circumferential direction among the plurality of grooves M (gap u) with reference to the direction in which the crank shaft 3 (drive shaft) rotates. A notch s1 is provided as a "discharge pipe insertion portion" through which Pb is inserted. That is, the size of the angle θ formed by the virtual plane Ta including the central axis Y and passing through the end point m2 and the virtual plane Tb including the central axis Y and passing near the upstream end of the discharge pipe Pb is 90 ° or more. ing.
Further, in the circumferential direction with respect to the direction in which the crank shaft 3 rotates, a predetermined notch or hole is not provided in the oil ring 13C (partition wall) between the end point m2 and the notch s1. It is preferable that the base plate 21a (see FIG. 1) and the frame 23 (see FIG. 1) are not provided with a predetermined flow path (groove). According to such a configuration, it becomes difficult for the refrigerant or the like that descends while swirling through the gap u and the annular gap k (see FIG. 1) to enter the inside of the oil ring 13C. Therefore, coupled with the fact that the oil ring 13C separates the upstream end e1 of the discharge pipe Pb from the gap u, the outflow of the lubricating oil through the discharge pipe Pb can be further suppressed.

Further, the air conditioner W (see FIG. 11) described in the third embodiment can be applied to various types of air conditioners such as room air conditioners, package air conditioners, and multi air conditioners for buildings.
Further, in the third embodiment, the air conditioner W (refrigeration 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 second embodiment can be applied to other "refrigerating cycle devices" such as refrigerators, water heaters, air-conditioned water heaters, and chillers.

Further, in each embodiment, the case where the refrigerant is compressed by the scroll compressor 100 has been described, but the present invention is not limited to this. That is, a predetermined gas other than the refrigerant may be compressed by the scroll compressor 100.
Moreover, each embodiment can be combined appropriately. For example, by combining the second embodiment and the third embodiment, the air conditioner W (third embodiment: see FIG. 11) uses a scroll compressor 100A with an outer cover specification (second embodiment: see FIG. 9). You may be prepared.

Further, 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 the one including all the configurations described. Further, it is possible to appropriately add / delete / replace other configurations with respect to a part of the configurations of each embodiment.
In addition, the above-mentioned mechanism and configuration show what is considered necessary for explanation, and do not necessarily show all the mechanisms and configurations in the product.

100, 100A Scroll Compressor 1 Closed container 1a Cylindrical chamber 1b, 1Ab Lid chamber 2 Compression mechanism 21 Fixed scroll 21a Base plate 212a Flange 22 Swing scroll 23 Frame 23a Peripheral 3 Crank shaft (drive shaft)
4 Main bearing (bearing)
5 Swivel bearing (bearing)
6 Motor 6a Stator 6b Rotor 8 Balance weight 13 Oil ring (bulkhead)
e1 upstream end (one end)
e2 Downstream end (other end)
G region M groove N oil flow path (first flow path)
Pa Suction pipe Pb Discharge pipe Q1 Peripheral end surface (peripheral end surface of lid chamber)
Q2 part (part of the inner wall surface of the lid chamber)
s1 Notch (discharge pipe insertion part)
s11 hole (discharge pipe insertion part)
Sm motor room (space)
Su space u gap

In order to solve the above-mentioned problems, the scroll compressor according to the present invention has a cylindrical tubular chamber, a lid chamber that closes the upper side of the tubular chamber, and a bottom chamber that closes the lower side of the tubular chamber. A swivel scroll having a closed container, a base plate fixed to the cylindrical chamber, a fixed scroll having a spiral fixed wrap, and a swirling swivel wrap forming a compression chamber together with the fixed wrap, and the swivel scroll. A frame, an electric motor having a stator and a rotor, and a drive shaft having a through hole for guiding lubricating oil and rotating integrally with the rotor, and being installed in the cylindrical chamber thereof. It includes a discharge pipe having one end located inside the closed container and the other end located outside the closed container, and a partition wall installed in the frame and separating the one end of the discharge pipe from the cylindrical chamber. The peripheral end surface of the lid chamber is in close contact with the surface of the flange portion of the base plate on the lid chamber side, or a part of the inner wall surface of the lid chamber is placed on the surface of the flange portion of the base plate on the lid chamber side. The flange portion of the base plate and the peripheral edge portion of the frame are provided with grooves recessed inward in the radial direction, and the space between the base plate and the lid chamber and the said. The space between the frame and the motor communicates through the gap of the groove, and in the vicinity of the upper end of the groove, a part of the gap is blocked by the lid chamber, and the stator Is provided with a first flow path for communicating one side and the other side of the stator in the axial direction of the drive shaft, and the flow path cross-sectional area of the gap at the upper end of the groove is the first flow path. It was decided to be smaller than the flow path cross-sectional area . Others will be described in the embodiment.

Claims (11)

A closed container having a cylindrical tubular chamber, a lid chamber that closes the upper side of the tubular chamber, and a bottom chamber that closes the lower side of the tubular chamber.
A base plate fixed to the tubular chamber, and a fixed scroll having a spiral fixing wrap,
A swirl scroll with a swirl swirl wrap that forms a compression chamber with the fixed wrap,
The frame that supports the swivel scroll and
Motors with stators and rotors,
It has a through hole for guiding lubricating oil, and is equipped with a drive shaft that rotates integrally with the rotor.
A discharge pipe installed in the tubular chamber, one end of which is located inside the closed container and the other end of which is located outside the closed container.
A partition wall installed in the frame and separating the one end of the discharge pipe and the tubular chamber is provided.
The peripheral end surface of the lid chamber is in close contact with the surface of the flange portion of the base plate on the lid chamber side, or a part of the inner wall surface of the lid chamber is on the surface of the flange portion of the base plate on the lid chamber side. Close and close
Grooves recessed inward in the radial direction are provided in the flange portion of the base plate and the peripheral edge portion of the frame.
The space between the base plate and the lid chamber and the space between the frame and the electric motor communicate with each other through the gap of the groove.
A scroll compressor in which a part of the gap is blocked by the lid chamber near the upper end of the groove. The stator is provided with a first flow path that allows one side and the other side of the stator to communicate with each other in the axial direction of the drive shaft.
The scroll compressor according to claim 1, wherein the flow path cross-sectional area of the gap at the upper end of the groove is smaller than the flow path cross-sectional area of the first flow path. Equipped with a balance weight that rotates integrally with the drive shaft,
The scroll compressor according to claim 1, wherein one end of the discharge pipe is located between the upper surface and the lower surface of the balance weight in the axial direction of the drive shaft. The feature is that the distance between the upper surface of the balance weight and the lower surface of the peripheral edge portion of the frame is shorter than the distance between the lower surface of the balance weight and the upper surface of the core back of the stator. The scroll compressor according to claim 3. The scroll compressor according to claim 4, wherein the plurality of bearings that pivotally support the drive shaft in the frame are composed of only journal bearings. The scroll compressor according to claim 1, wherein a notch or a hole is provided in a lower portion of the partition wall as a discharge pipe insertion portion through which the discharge pipe is inserted. The scroll compressor according to claim 6, wherein in the partition wall, at least a part above the discharge pipe is provided with a region in which the partition wall exists over the entire circumference in the circumferential direction. .. The discharge pipe insertion portion is provided at a position 90 ° or more away from the end point located on the most downstream side in the circumferential direction among the plurality of grooves with reference to the direction in which the drive shaft rotates.
In the circumferential direction with respect to the direction in which the drive shaft rotates, the partition wall is not provided with a predetermined notch or hole between the end point and the discharge pipe insertion portion, and the base plate and the said plate. The scroll compressor according to claim 6, wherein the frame is not provided with a predetermined flow path. The outer peripheral surface near the lower end of the lid chamber is in close contact with the inner peripheral surface near the upper end of the tubular chamber.
The scroll compressor according to claim 1, wherein a portion corresponding to the gap in the circumferential direction faces the gap at the lower end of the lid chamber. The distance between the wall surface of the groove and the tubular chamber is longer than the distance between the lower end of the lid chamber and the flange portion of the base plate.
The scroll compressor according to claim 9, wherein the distance between the cylinder chamber and the partition wall is longer than the distance between the wall surface of the groove and the cylinder chamber. The scroll compressor according to any one of claims 1 to 10 is provided.
A refrigerating cycle apparatus including a refrigerant circuit in which a refrigerant circulates sequentially through the scroll compressor, a condenser, an expansion valve, and an evaporator.

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