WO2021095151A1

WO2021095151A1 - Compressor and air conditioner

Info

Publication number: WO2021095151A1
Application number: PCT/JP2019/044481
Authority: WO
Inventors: 隆雅足立; 太田　裕樹; 駿田坂; 村上　晃啓
Original assignee: 日立ジョンソンコントロールズ空調株式会社
Priority date: 2019-11-13
Filing date: 2019-11-13
Publication date: 2021-05-20
Also published as: CN115324899B; JP6772399B1; CN114450488B; CN114450488A; JPWO2021095151A1; CN115324899A

Abstract

Provided are a compressor and the like in which outflow of lubricating oil is suppressed. A compressor (100) is provided with: an electric motor (7) including a stator (7a) and a rotor (7b); a crankshaft (4) which rotates integrally with the rotor (7b); a compression mechanism unit (2) which compresses a refrigerant concomitant with the rotation of the crankshaft (4); an arc-shaped or cylindrical balance weight (12) situated on the rotor (7b); and a hermetically sealed container (1) in which the lubricating oil is sealed. The balance weight (12) has a plurality of notched portions which are recessed radially inward from an outer circumferential surface, wherein the plurality of notched portions are each provided in the circumferential direction of the balance weight (12), and open in a space (G1) inside the hermetically sealed container (1).

Description

Compressor and air conditioner

The present invention relates to a compressor or the like.

As a balance weight for suppressing the vibration of the compressor, for example, Patent Document 1 describes an arc-shaped balance weight in which a plurality of thin plates are laminated.

Japanese Unexamined Patent Publication No. 2000-116080

By the way, the compressor is usually filled with lubricating oil to improve the lubricity of the sliding part and the sealing property of the compression chamber. In such a compressor, the lubricating oil stored as an oil pool in the closed container rises through the oil supply passage of the crankshaft, lubricates the sliding parts such as bearings, and then the compression mechanism part and the closed container. It descends through the gap between the motors and the gap between the electric motor and the closed container, and is returned to the oil sump in the closed container.

However, for example, the mist-like lubricating oil may be blown up through the gap between the stator and the rotor of the motor, and the lubricating oil may flow out from the compressor through the discharge pipe. In Patent Document 1 described above, the balance weight installed on the rotor has a smooth flush shape on the upper surface, the lower surface, and the peripheral surface. When a balance weight having such a shape is used, the flow of the lubricating oil blown up through the gap between the stator and the rotor is hardly obstructed by the balance weight, and the lubricating oil flows out through the discharge pipe. It will be easier. As a result, the compressor may be under-lubricated and the efficiency of the refrigeration cycle may be reduced.

Therefore, an object of the present invention is to provide a compressor or the like that suppresses the outflow of lubricating oil.

In order to solve the above-mentioned problems, the present invention has a plurality of notches in which the balance weight is recessed radially inward from the outer peripheral surface, and each of the plurality of notches is in the circumferential direction of the balance weight. It was decided that the space inside the closed container would be open.

According to the present invention, it is possible to provide a compressor or the like that suppresses the outflow of lubricating oil.

It is a vertical sectional view of the compressor which concerns on 1st Embodiment of this invention. It is sectional drawing of the rotor of the electric motor provided in the compressor which concerns on 1st Embodiment of this invention. It is a vertical cross-sectional view including the electric motor and the balance weight of the compressor which concerns on 1st Embodiment of this invention. It is a perspective view of the balance weight provided in the compressor which concerns on 1st Embodiment of this invention. It is explanatory drawing (plan view) about the arrangement of the concave part, the notch part, the oil escape hole, etc. of the balance weight provided in the compressor which concerns on 1st Embodiment of this invention. It is a bottom view of the balance weight provided in the compressor which concerns on 1st Embodiment of this invention. It is explanatory drawing (plan view) of the balance weight provided in the compressor which concerns on 1st modification which concerns on 1st Embodiment of this invention. It is an exploded perspective view of the balance weight provided in the compressor which concerns on the 2nd modification which concerns on 1st Embodiment of this invention. It is a perspective view of the balance weight provided in the compressor which concerns on 2nd Embodiment of this invention. It is a perspective view of the back side of the balance weight provided in the compressor which concerns on 2nd Embodiment of this invention. It is a perspective view of the balance weight provided in the compressor which concerns on 3rd Embodiment of this invention. It is a perspective view of the back side of the balance weight provided in the compressor which concerns on 3rd Embodiment of this invention. It is a top view of the balance weight provided in the compressor which concerns on 4th Embodiment of this invention. It is a block diagram of the air conditioner which concerns on 5th Embodiment of this invention.

<< First Embodiment >>
<Compressor configuration>
FIG. 1 is a vertical cross-sectional view of the compressor 100 according to the first embodiment.
The compressor 100 shown in FIG. 1 is a device that compresses a gaseous refrigerant. As shown in FIG. 1, the compressor 100 includes a closed container 1, a compression mechanism 2, a frame 3, a crankshaft 4 (drive shaft), a main bearing 5, a swivel bearing 6, and an electric motor 7. It has. Further, the compressor 100 includes an old dam ring 8, a subframe 9, an auxiliary bearing 10, and

balance weights

11 and 12 in addition to the above-described configuration.

The closed container 1 is a shell-shaped container that houses the motor 7, the crankshaft 4, the compression mechanism 2, the

balance weights

11, 12, and the like, and is substantially sealed. Lubricating oil for improving the lubricity of the compressor 100 is sealed in the closed container 1, and is stored as an oil sump M at the bottom of the closed container 1. The closed container 1 includes a cylindrical tubular chamber 1a, a lid chamber 1b welded to the upper part of the tubular chamber 1a, and a bottom chamber 1c welded to the lower part of the tubular chamber 1a.

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 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 compressor 100.

The compression mechanism unit 2 is a mechanism that compresses the refrigerant as the crankshaft 4 rotates. The compression mechanism unit 2 includes a fixed scroll 21 and a swivel scroll 22, 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 includes a thick base plate 21a having a disk shape and a spiral wrap 21b erected under the base plate 21a. A suction chamber H in which the refrigerant is guided via the suction pipe Pa is provided near the peripheral edge of the base plate 21a.

The swivel scroll 22 is a moving member that forms a compression chamber C between the swivel scroll 22 and the fixed scroll 21 by the swivel. The swivel scroll 22 includes a disc-shaped base plate 22a, a spiral wrap 22b erected on the base plate 22a, and a boss portion 22c fitted to the upper end portion of the crankshaft 4. .. As shown in FIG. 1, the wrap 22b extends above the base plate 22a, while the boss portion 22c extends below the base plate 22a.

Then, a predetermined compression chamber C is formed between the spiral wrap 21b of the fixed scroll 21 and the spiral wrap 22b of the swirl scroll 22. The compression chamber C is a space for compressing the gaseous refrigerant, and is formed on the outer line side and the inner line side of the lap 22b of the swivel scroll 22, respectively. 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.

The frame 3 shown in FIG. 1 is a member that supports the swivel scroll 22 and fixes the main bearing 5. The frame 3 has a substantially rotationally symmetric shape and is fastened to the lower side of the fixed scroll 21. The frame 3 is provided with a hole through which the crankshaft 4 is inserted (not shown by reference numeral in FIG. 1).
The crankshaft 4 is a shaft that rotates integrally with the rotor 7b of the motor 7, and extends in the vertical direction. As shown in FIG. 1, the crankshaft 4 includes a main shaft 4a, a flange portion 4b connected to the upper side of the main shaft 4a, and an eccentric portion 4c connected to the upper side of the flange portion 4b.

The spindle 4a is coaxially fixed to the rotor 7b of the electric motor 7, and rotates integrally with the rotor 7b. The flange portion 4b has a columnar shape and is provided coaxially with the spindle 4a between the spindle 4a and the eccentric portion 4c. The diameter of the flange portion 4b is larger than the diameter of the main shaft 4a and the eccentric portion 4c.
The eccentric portion 4c is an axis that rotates while being eccentric with respect to the main shaft 4a, and is fitted to the boss portion 22c of the swivel scroll 22 as described above. Then, the eccentric portion 4c rotates while being eccentric, so that the swivel scroll 22 turns.

The main bearing 5 rotatably supports the upper portion of the main shaft 4a, and is fixed to the peripheral wall surface of a hole (not shown by a reference numeral in FIG. 1) of the frame 3.
The swivel bearing 6 rotatably supports the eccentric portion 4c and is fixed to the inner peripheral wall of the boss portion 22c.

Inside the crankshaft 4, a lubrication passage 4d through which lubricating oil flows is provided in the vertical direction. The lubricating oil flowing through the oil supply passage 4d is guided to the main bearing 5, the swivel bearing 6, the auxiliary bearing 10, and the like in addition to the compression mechanism portion 2.

The motor 7 is a drive source for rotating the crankshaft 4, and is arranged below the frame 3. As shown in FIG. 1, the electric motor 7 includes a stator 7a, a rotor 7b, and a winding 7c. The stator 7a is a cylindrical member formed by laminating electromagnetic steel sheets, and is fixed to the inner peripheral wall of the tubular chamber 1a. The rotor 7b is a cylindrical member formed by laminating electromagnetic steel sheets, and is arranged inside the stator 7a in the radial direction. The crankshaft 4 is fixed to the rotor 7b by press fitting or the like. The winding 7c is a wiring through which an electric current flows, is wound in a predetermined manner, and is installed in the stator 7a.

The Oldam ring 8 is a ring-shaped member that receives the eccentric rotation of the eccentric portion 4c and rotates the swivel scroll 22 without rotating. The old dam ring 8 is provided between the swivel scroll 22 and the frame 3.

The

balance weights

11 and 12 are arc-shaped members that alleviate the unbalance of rotation caused by the compression mechanism unit 2. In the example of FIG. 1, one balance weight 11 is installed on the outer peripheral wall of the flange portion 4b, and the other balance weight 12 is installed below the rotor 7b of the motor 7. The relative positional relationship between the

balance weights

11 and 12 is appropriately set based on prior experiments and simulations. The main feature of this embodiment is the configuration of the balance weight 12 installed under the rotor 7b, and the details of the balance weight 12 will be described later.

The subframe 9 shown in FIG. 1 rotatably supports the lower portion of the crankshaft 4, and is fixed to the inner peripheral wall of the closed container 1.
The sub-bearing 10 rotatably supports the lower portion of the crankshaft 4, and is fixed to the peripheral wall surface of a hole (not shown) of the sub-frame 9.

Further, although not shown in FIG. 1, a thin plate-shaped metal piece (not shown) twisted and bent at an upstream end (that is, near the lower end of the crankshaft 4) of the oil supply passage 4d of the crankshaft 4 ) Is installed. Then, the metal piece is rotated integrally with the crankshaft 4, so that the lubricating oil is pumped up through the oil supply passage 4d.

Then, when the swivel scroll 22 is swiveled by the drive of the electric motor 7, the volume of the compression chambers C formed one after another is reduced accordingly, and the gaseous refrigerant is compressed. The compressed refrigerant is discharged into the upper space in the closed container 1 through the discharge port V of the fixed scroll 21, and further, through the gap between the frame 3 and the cylinder chamber 1a, the compression mechanism unit 2 Guided to the bottom. Therefore, the spaces above and below the compression mechanism 2 are filled with gaseous refrigerants that are substantially equal to the discharge pressure, respectively. The refrigerant guided to the lower side of the compression mechanism portion 2 is guided to a condenser (not shown) via a discharge pipe Pb or the like, and circulates in a predetermined refrigeration cycle.
The configuration of the compressor 100 shown in FIG. 1 is an example, and the present invention is not limited to this.

FIG. 2 is a cross-sectional view of the rotor 7b of the motor 7.
The cylindrical rotor 7b shown in FIG. 2 includes a plurality of electromagnetic steel sheets 71b laminated in the axial direction, six permanent magnets 72b (magnets), and a pair of

end plates

72c and 72d (see FIG. 3). I have. Six magnet insertion holes h1 into which thin plate rectangular permanent magnets 72b are inserted are provided near the outer peripheral edges of the plurality of electromagnetic steel plates 71b at substantially equal intervals in the circumferential direction. Further, the rotor 7b is provided with a plurality of rivet through holes h2 (six in the example of FIG. 2) for penetrating the rivet 13, which will be described later, in the radial direction with respect to the magnet insertion hole h1.

FIG. 3 is a vertical cross-sectional view including the motor 7 and the balance weight 12.
As shown in FIG. 3, an annular end plate 72c is installed on the upper surface of the rotor 7b (the upper surface of the electromagnetic steel sheet 71b having the highest installation position). On the other hand, another annular end plate 72d is installed on the lower surface of the rotor 7b (the lower surface of the electromagnetic steel sheet 71b having the lowest installation position). The pair of

end plates

72c and 72d close the magnet insertion hole h1 (see FIG. 2) to prevent the permanent magnet 72b from coming off the rotor 7b.

The balance weight 12 is a member that alleviates the unbalance of rotation caused by the compression mechanism portion 2 and suppresses the vibration of the compressor 100, and is installed on the lower surface of the end plate 72d. In the present embodiment, a case where an iron material (magnetic material) having a relatively high density and being inexpensive is used as a constituent material of the balance weight 12 will be described.

The rivet 13 shown in FIG. 3 fixes the

end plates

72c and 72d and the balance weight 12 to the rotor 7b. These rivets 13 penetrate the above-mentioned rivet through holes h2 and the like (see FIG. 2) and are crimped and fixed. Next, the configuration of the balance weight 12 will be described with reference to FIG. 4 and the like.

FIG. 4 is a perspective view of the balance weight 12 included in the compressor.
As shown in FIG. 4, the balance weight 12 has an arc shape and has a predetermined thickness in the height direction. Further, the balance weight 12 includes three recesses 12a recessed from the upper surface T in the axial direction of the rotor 7b, and three notches 12b recessed radially inward from the outer peripheral surface.
The upper surface T of the balance weight 12 is an end surface on the rotor 7b side (see FIG. 3), and at least a part thereof is in contact with the end plate 72d (see FIG. 3). On the other hand, the lower surface B (see FIG. 5B) of the balance weight 12 is an end face on the opposite side of the rotor 7b (see FIG. 3) and has a flat shape.

Explaining from another point of view, the balance weight 12 has the following configuration. That is, the balance weight 12 cuts a virtual cylindrical member (not shown) having a predetermined thickness in substantially half on a predetermined plane (not shown) parallel to the central axis Z (see FIG. 3). Further, the structure is provided with a recess 12a and a notch 12b. Further, the balance weight 12 includes a rib 12c (first rib), an oil escape hole h3 (first hole), and a rivet through hole h4.

As described above, the recess 12a is a portion recessed downward in the axial direction from the upper surface T of the balance weight 12, and is mainly used for adjusting the weight of the balance weight 12. For example, when the weight of the balance weight 12 is reduced, it is appropriately designed at the design stage so that the bottom surface of the recess 12a becomes deeper with respect to the upper surface T of the balance weight 12.

The weight of the balance weight 12 can be adjusted by adjusting the depth of the notch 12b, but as will be described later, the notch 12b mainly has a function of applying a lateral force to the mist-like lubricating oil. It has a function of suppressing leakage of magnetic flux of the permanent magnet 72b.

In the example shown in FIG. 4, the inner wall surface of the recess 12a includes a pair of

peripheral wall surfaces

121a, 122a, a pair of

side surfaces

123a, 124a, and a bottom surface 125a. The pair of

peripheral wall surfaces

121a and 122a described above have an arc shape in a plan view with the central axis Z of the rotor 7b (see FIG. 3) as the center. The other peripheral wall surface 122a is located on the outer side in the radial direction than the one peripheral wall surface 121a.

The pair of

side surfaces

123a and 124a are planar wall surfaces connected to the

peripheral wall surfaces

121a and 122a, and are provided in the radial direction in a plan view with reference to the central axis Z of the rotor 7b (see FIG. 3). On the other hand, the bottom surface 125a of the recess 12a is flat. In the example of FIG. 4, each of the three recesses 12a has the same shape.

As shown in FIG. 4, the three recesses 12a are provided at substantially equal intervals in the circumferential direction, and are provided inside the notch 12b (first notch) in the radial direction. Further, the recess 12a and the notch 12b are arranged in the radial direction. The end surface (that is, the upper surface T) of the balance weight 12 on the rotor 7b side is in contact with the rotor 7b around the recess 12a (see FIG. 3).

Each recess 12a is provided with one oil relief hole h3 (first hole) having a predetermined diameter. These oil relief holes h3 are holes for releasing oil accumulated in the recess 12a, and penetrate the recess 12a in the axial direction of the rotor 7b. The diameter of the oil relief hole h3 is smaller than the diameter of the rivet through hole h4 described later, and is smaller than the diameter of the rivet 13 (see FIG. 3) (the diameter of the portion penetrating the rotor 7b).
The oil release hole h3 opens in the space Ga (see FIG. 3) between the recess 12a and the rotor 7b, and also in the space G1 (see FIG. 1) in the closed container 1, or the balance weight 12 It is open to the lower surface B (the surface opposite to the upper surface T, which is the surface in contact with the rotor 7b). Therefore, the space Ga (see FIG. 3) between the recess 12a and the rotor 7b communicates with the space G1 in the closed container 1 through the oil escape hole h3.

By providing such an oil release hole h3, even if the lubricating oil enters the recess 12a through a minute gap between the balance weight 12 and the end plate 72d (see FIG. 3), the lubricating oil releases the oil. It flows down from the recess 12a to the lower side of the balance weight 12 through the hole h3. Therefore, it is possible to prevent the weight of the lubricating oil that has entered the recess 12a from adversely affecting the function of the balance weight 12 (alleviating the imbalance in rotation).

Each of the three notched portions 12b shown in FIG. 4 is a portion recessed radially inward from the outer peripheral surface of the balance weight 12, and is provided on the outer peripheral edge portion of the balance weight 12 on the rotor 7b side (see FIG. 3). Has been done. That is, each of the three notches 12b is provided in the circumferential direction of the balance weight 12 and opens into the space inside the closed container 1. In the example of FIG. 4, the wall surface of the recess 12a includes a peripheral wall surface 121b, a pair of side surfaces 122b and 123b, and a bottom surface 124b.

First, the peripheral wall surface 121b has an arc shape in a plan view with the central axis Z of the rotor 7b (see FIG. 3) as the center. The pair of side surfaces 122b and 123b are connected to the peripheral wall surface 121b described above, and are provided in the radial direction in a plan view with reference to the central axis Z of the rotor 7b (see FIG. 3). Further, the bottom surface 124b of the notch portion 12b is flat. In the example of FIG. 4, each of the three notches 12b has the same shape.

Further, in each notch portion 12b, the wall surface closest to the central axis Z of the rotor 7b (see FIG. 3) (that is, the peripheral wall surface 121b) is located radially outside the inner peripheral surface of the balance weight 12. There is. According to such a configuration, since the radial inner portion of the notch portion 12b occupies a part of the weight of the balance weight 12, the axial length of the balance weight 12 can be made relatively short. Further, the balance weight 12 is stably held in the radial inner portion of the notch portion 12b.

In the example of FIG. 4, the axial depth of the recess 12a and the axial depth of the notch 12b are the same, but they may be different.
As shown in FIG. 4, three notches 12b are provided at substantially equal intervals in the circumferential direction. Further, in the outer peripheral edge portion of the balance weight 12 on the rotor 7b side (see FIG. 3), a predetermined gap Gb (see FIG. 3) is formed between the portion where the notch portion 12b is provided and the rotor 7b. It is provided.

Although details will be described later, the notch 12b includes a region R (see FIG. 5A) when the permanent magnet 72b of the rotor 7b is projected in the axial direction. As a result, even when the balance weight 12 is made of a magnetic material such as an iron material, it is possible to prevent the magnetic flux of the permanent magnet 72b of the rotor 7b from leaking to the balance weight 12 side via the end plate 72d (see FIG. 3). .. This is because there is a gap Gb (see FIG. 3) between the notch 12b and the end plate 72d (see FIG. 3), which makes it difficult for magnetic flux to pass through. As a result, leakage of magnetic flux from the electric motor 7 is suppressed, so that the electric motor 7 can be driven with high efficiency. The axial depth of the notch portion 12b is appropriately adjusted at the design stage to the extent that leakage of magnetic flux from the electric motor 7 is suppressed.

As shown in FIG. 4, two ribs 12c (first ribs) extending in the radial direction are provided between the recesses 12a adjacent to each other in the circumferential direction and between the notches 12b adjacent to each other in the circumferential direction. .. The radial outer wall surface of these ribs 12c is flush with the outer peripheral surface of the balance weight 12. Ribs 12c are also provided at both ends of the balance weight 12 in the circumferential direction. The end face of each rib 12c on the rotor 7b side (that is, a part of the upper surface T) is in contact with the rotor 7b. More specifically, the upper surface of each rib 12c is in contact with the lower surface of the end plate 72d (see FIG. 3) of the rotor 7b. Further, in the example of FIG. 4, one rivet through hole h4 for penetrating the rivet 13 (see FIG. 3) is provided in each of the four ribs 12c.

In the example of FIG. 4, the circumferential length of the rib 12c (thickness in the circumferential direction) is shorter than the circumferential length of the recess 12a and shorter than the circumferential length of the notch 12b. .. The circumferential length of the recess 12a is the length of the outer peripheral edge (arc) of the bottom surface 125a of the recess 12a. The circumferential length of the notch portion 12b is the length of the outer peripheral side edge (arc) of the bottom surface 124b of the notch portion 12b.
Further, in the example of FIG. 4, in the rib 12c, the radial length of the portion between the recess 12a and the notch 12b is shorter than the radial length of the recess 12a, and the radial length of the notch 12b is short. It is shorter than the length of.

By providing such a rib 12c, the balance weight 12 can be stably held. Further, when the balance weight 12 is rotating together with the rotor 7b, a lateral force acts on the mist-like lubricating oil by the rib 12c (in other words, by the notch 12b), and the vertical force in the velocity vector of the lubricating oil is applied. The ratio of velocity components in the direction and lateral direction changes. Next, the flow of such lubricating oil will be described in detail.

When the balance weight 12 rotates together with the rotor 7b, the mist-like lubricating oil existing under the motor 7 (see FIG. 1) is exposed to the wall surface of the notch 12b (particularly, the side surface opposite to the direction of rotation). ), A lateral force acts. Here, focusing on the velocity vector of the mist-like lubricating oil, the velocity component in the horizontal direction becomes relatively large with respect to the velocity component in the vertical direction. That is, assuming that the mist-like lubricating oil is moving in the closed container 1 (see FIG. 1) with a velocity vector of a predetermined magnitude, the lateral velocity component occupying the magnitude of the velocity vector is large. On the other hand, the velocity component in the vertical direction becomes smaller.

Then, the flow that the mist-like lubricating oil moves upward through the gap between the stator 7a (see FIG. 1) and the rotor 7b (see FIG. 1) is less likely to occur. As a result, the outflow of lubricating oil through the discharge pipe Pb (see FIG. 1) is suppressed, so that each sliding portion of the compression mechanism portion 2 is satisfactorily lubricated, and the sealing property of the compression chamber C is ensured. Lubrication.

FIG. 5A is an explanatory view (plan view) regarding the arrangement of the recess 12a of the balance weight 12, the notch 12b, the oil relief hole h3, and the like.
Hereinafter, a predetermined arc including a group of points at an intermediate position of the concave portion 12a in the radial direction is referred to as an intermediate arc J (two-dot chain line in FIG. 5A). In the example shown in FIG. 5A, the three recesses 12a are arranged side by side in the circumferential direction so that their intermediate arcs J substantially coincide with each other. Further, the oil relief hole h3 provided in the recess 12a is arranged radially outside the intermediate arc J. In other words, the oil relief hole h3 is provided radially outside the intermediate position of the recess 12a in the radial direction.

When the balance weight 12 rotates together with the rotor 7b while the lubricating oil is accumulated in the recess 12a (see the arrow indicating the direction of rotation in FIG. 5A), the lubricating oil is centrifugally outward in the radial direction. Move to. Here, since the oil relief hole h3 is provided radially outside the intermediate arc J of the recess 12a, the lubricating oil that has moved outward in the radial direction due to centrifugal force passes through the oil relief hole h3 and is a balance weight. It is easy to escape to the lower side of 12.

Further, as described above, the notch 12b (first notch) includes the region R when the permanent magnet 72b (magnet) embedded in the rotor 7b is projected in the axial direction of the rotor 7b. There is. Therefore, even when the balance weight 12 is made of a magnetic material such as an iron material, it is possible to prevent the magnetic flux of the permanent magnet 72b from leaking to the balance weight 12 side.
The positional relationship between the permanent magnet 72b and the notch 12b is not limited to this. For example, the region R when the permanent magnet 72b is projected in the axial direction of the rotor 7b may be included in at least a part (preferably all) of the notch portion 12b. When the region R is included in at least a part of the notch portion 12b in this way, both ends in the circumferential direction of the region R are included in the notch portion 12b, while the central portion in the circumferential direction of the region R is included in the notch portion 12b. It may not be configured. Even with such a configuration, leakage of magnetic flux of the permanent magnet 72b can be suppressed.

It is preferable that the region R when the permanent magnet 72b is projected in the axial direction is close to the radial inner edge of the notch portion 12b (first notch portion). In the example of FIG. 5A, the region R when the permanent magnet 72b is projected in the axial direction is in contact with the edge of the notch portion 12b. More specifically, on the side surface of the permanent magnet 72b on the central axis Z side, the position F closest to the central axis Z of the rotor 7b is in contact with the radial inner edge of the notch 12b. Such a configuration is also included in the matter that "the region R when the permanent magnet 72b is projected in the axial direction is included in the notch portion 12b".

By defining the positional relationship between the notch 12b and the permanent magnet 72b in this way, it is possible to minimize the length of the notch 12b denting inward in the radial direction while suppressing the leakage of magnetic flux from the permanent magnet 72b. Can be done. Therefore, when designing the balance weight 12, the length of the balance weight 12 in the axial direction can be short, so that the compressor 100 (see FIG. 1) can be made compact.

As shown in FIG. 4, the notch portion 12b is formed on the outer peripheral edge portion on the rotor 7b side (see FIG. 3) rather than forming the notch portion 12b over the entire axial length of the balance weight 12. Is preferable. This is because the region located on the outer side of the balance weight 12 in the radial direction has a larger moment of inertia during rotation and contributes more to the function of the balance weight 12 to maintain a good rotational balance.

FIG. 5B is a bottom view of the balance weight 12 included in the compressor.
As shown in FIG. 5B, the lower surface B of the balance weight 12 is flat. Further, the oil escape hole h3 described above is opened on the lower surface B of the balance weight 12, and the rivet through hole h4 is opened.

<Effect>
According to the first embodiment, since a lateral force acts on the mist-like lubricating oil from the wall surface of the notch 12b of the balance weight 12 (see FIG. 4), it becomes difficult for the lubricating oil to move in the vertical direction. .. As a result, the flow of the lubricating oil blown up in the vertical direction is suppressed, so that the outflow of the lubricating oil through the discharge pipe Pb can be suppressed.

Further, a predetermined gap Gb is provided between the portion of the balance weight 12 where the notch 12b (see FIG. 3) is provided and the rotor 7b, and the permanent magnet 72b is projected in the axial direction. The region R of the case (see FIG. 5A) is included in the notch 12b. Therefore, even when the balance weight 12 of a magnetic material such as an iron material is used, the leakage of magnetic flux can be suppressed. As described above, according to the first embodiment, it is possible to reduce the manufacturing cost of the compressor 100 (see FIG. 1) while suppressing the decrease in the efficiency of the electric motor 7 (see FIG. 1). Further, since the leakage of magnetic flux can be suppressed without increasing the wall thickness of the end plate 72d (see FIG. 3), there is almost no possibility that the size of the compressor 100 will increase.

Further, by providing the oil relief hole h3 in the recess 12a (see FIG. 4) of the balance weight 12, the lubricating oil that has entered the recess 12a can be released to the lower side of the balance weight 12. Further, since the oil relief hole h3 is provided on the outer side in the radial direction from the intermediate arc J (see FIG. 5A), the lubricating oil that has moved outward in the radial direction by centrifugal force passes through the oil relief hole h3. , It becomes easy to escape from the recess 12a.

<< First Modification Example Regarding the First Embodiment >>
FIG. 6 is an explanatory view (plan view) of the balance weight 12A included in the compressor according to the first modification.
As shown in FIG. 6, the oil relief hole h3 (first hole) provided in the recess 12a of the balance weight 12A is provided in the recess 12a on the side opposite to the direction in which the rotor 7b rotates in the circumferential direction. You may do so. Here, the "opposite side" means a region between an intermediate position in the concave portion 12a in the circumferential direction and a side surface in the concave portion 12a opposite to the direction in which the rotor 7b rotates.

As a result, when the balance weight 12A is rotating integrally with the rotor 7b (see FIG. 3), the lubricating oil accumulated in the recess 12a is biased to the side opposite to the direction in which the rotor 7b rotates due to its inertia. Is distributed. Therefore, by providing the oil release hole h3 in the recess 12a on the side opposite to the direction in which the rotor 7b rotates, the lubricating oil can be easily released from the recess 12a through the oil release hole h3.

The arrangement of the oil relief hole h3 described in FIG. 5A of the first embodiment may be combined with the arrangement of the oil relief hole h3 described in FIG. 6 as a first modification. That is, in the recess 12a, the oil escape hole h3 may be provided on the radial side of the intermediate arc J (see FIG. 5A) and on the side opposite to the direction in which the rotor 7b rotates. As a result, the lubricating oil that moves outward in the radial direction by centrifugal force and is distributed unevenly in the direction opposite to the direction of rotation of the rotor 7b due to inertia escapes from the recess 12a through the oil relief hole h3. It becomes easy to be done.

<< Second variant of the first embodiment >>
FIG. 7 is an exploded perspective view of the balance weight 12B included in the compressor according to the second modification.
As shown in FIG. 7, the balance weight 12B is not integrally formed as a whole, but as a plurality of steel plates laminated in the axial direction of the rotor 7b, for example, three first steel plates 121 and six. The second steel plate 122 of the above may be provided.

The first steel plate 121 is provided with a notch 12b and a rivet through hole h4, and further, a hole h5 for forming a recess 12a (see FIG. 4) and a protrusion for forming a rib 12c (see FIG. 4). A portion 121c is provided.
In addition to ensuring the contact area and strength of the protrusion 121c with the rotor 7b (see FIG. 3), the protrusion 121c can be positioned in the circumferential direction and the radial direction when the first steel plate 121 and the second steel plate 122 are laminated, and has a diameter. Used to receive directional pressure. As shown in FIG. 7, each of the three first steel plates 121 has the same shape.

The second steel plate 122 is provided with an oil escape hole h3 and a rivet through hole h4. The second steel plate 122 is not provided with a notch 12b like the first steel plate 121, and is not provided with a hole h5 for forming a recess 12a (see FIG. 4). The six second steel plates 122 each have the same shape.

In the example of FIG. 7, the second laminated body 12t formed by laminating six second steel plates 122 is superposed on the lower side of the first laminated body 12s formed by laminating three first steel plates 121. Then, the balance weight 12B having the same shape as that of the first embodiment (see FIG. 4) is formed.

Since the balance weight 12B is made of laminated steel plates in this way, for example, the depth of the recess 12a (see FIG. 4) can be adjusted or the rotor can be adjusted by appropriately changing the number of laminated steel plates 121. The length of the gap Gb between 7b (see FIG. 3) and the bottom surface of the notch 12b (see FIG. 3) can be adjusted. Therefore, when changing the depth of the recess 12a (see FIG. 1) and the notch 12b of the balance weight 12B according to the specifications of the compressor 100 (see FIG. 1), it is common to the first steel plate 121 and the second steel plate 122. Can be used, so that the manufacturing cost of the balance weight 12B can be reduced.

As a first steel plate (not shown) of a type different from the first steel plate 121 shown in FIG. 7, a notch 12b is provided, but a hole h5 corresponding to a recess 12a (see FIG. 4) is provided. A steel plate that has not been used may be inserted between the first steel plate 121 and the second steel plate 122. Further, as a second steel plate (not shown) of a type different from the second steel plate 122 shown in FIG. 7, although the notch 12b is not provided, the hole h5 corresponding to the recess 12a (see FIG. 4) is provided. The steel plate may be inserted between the first steel plate 121 and the second steel plate 122. Thereby, the depth of the notch portion 12b and the depth of the recess 12a can be adjusted independently.

<< Second Embodiment >>
The balance weight 12C (see FIGS. 8A and 8B) according to the second embodiment is the first embodiment in that the first steel plate 121 and the second steel plate 122 are alternately laminated in the axial direction. It is different from the modification of No. 2 (see FIG. 7). In addition to the overall configuration of the compressor 100 (see FIG. 1), the configurations of the first steel plate 121 and the second steel plate 122 are the same as those of the second modification of the first embodiment (see FIG. 7). The same is true. Therefore, a part different from the second modification of the first embodiment will be described, and the description of the overlapping part will be omitted.

FIG. 8A is a perspective view of the balance weight 12C included in the compressor according to the second embodiment.
As shown in FIG. 8A, the balance weight 12C has a configuration in which the first steel plate 121 and the second steel plate 122 are alternately laminated in the axial direction of the rotor 7b. In the example of FIG. 8A, eight first steel plates 121 and eight second steel plates 122 are used as the steel plates constituting the balance weight 12C, but the number of each steel plate is limited to this. It's not a thing.

As described above, the first steel plate 121 is provided with a notch 12b, a rivet through hole h4, a protruding portion 121c (first rib), and a hole h5 for forming a recess 12a (see FIG. 4). Has been done. On the other hand, the second steel plate 122 is provided with an oil escape hole h3 and a rivet through hole h4, but is not provided with a notch 12b or a hole h5.

When the balance weight 12C having such a configuration rotates together with the rotor 7b (see FIG. 1), the wall surface (side surface opposite to the direction of rotation) of the notch portion 12b of each first steel plate 121 becomes a mist-like lubricating oil. A lateral force acts on the lubricating oil from the balance weight 12C. As a result, the vertical flow of the lubricating oil is suppressed, and by extension, the outflow of the lubricating oil through the discharge pipe Pb (see FIG. 1) is suppressed.

Further, in the balance weight 12C shown in FIG. 8A, since the first steel plate 121 and the second steel plate 122 are alternately laminated in the axial direction, the surface area of the balance weight 12C is larger than that of the first embodiment (see FIG. 4). It's getting bigger. Therefore, during the driving of the motor 7 (see FIG. 1), the amount of lubricating oil adhering to the balance weight 12C due to its surface tension is larger than that in the first embodiment. As a result, the amount of mist-like lubricating oil floating under the balance weight 12C is reduced, and the lubricating oil is passed through the gap between the stator 7a (see FIG. 1) and the rotor 7b (see FIG. 1). It becomes difficult for the oil to blow up. Therefore, the outflow of lubricating oil through the discharge pipe Pb (see FIG. 1) is suppressed.

Further, as shown in FIG. 8A, in the balance way 12C, the first steel plate 121 is provided at a position (that is, the upper end portion) closest to the rotor 7b in the axial direction of the rotor 7b (see FIG. 1). There is. In such a configuration, a permanent magnet 72b (magnet) embedded in the rotor 7b is axially formed in the notch 12b of the first steel plate 121 located closest to the rotor 7b (see FIG. 1) in the axial direction. It is preferable that the region R (see FIG. 5A) when projected in is included. As a result, even when the balance weight 12C is made of a magnetic material such as an iron material, it is possible to prevent the magnetic flux of the permanent magnet 72b of the rotor 7b from leaking to the balance weight 12C side via the end plate 72d (see FIG. 3). ..

FIG. 8B is a perspective view of the back side of the balance weight 12C provided in the compressor.
That is, FIG. 8B is a perspective view of the balance weight 12C of FIG. 8A looking up obliquely from below. In the example of FIG. 8, in the balance weight 12C, the second steel plate 122 is installed at the position farthest from the rotor 7b in the axial direction (that is, the lower end portion), and the lower surface of the balance weight 12C is flat.

<Effect>
According to the second embodiment, since the first steel plate 121 and the second steel plate 122 are alternately laminated in the axial direction, the surface area of the balance weight 12C can be increased. Therefore, while the motor 7 (see FIG. 1) is being driven, a large amount of lubricating oil adheres to the balance weight 12C, and the amount of mist-like lubricating oil floating under the balance weight 12C is reduced. As a result, the lubricating oil is less likely to be blown up through the gap between the stator 7a (see FIG. 1) and the rotor 7b (see FIG. 1), and eventually through the discharge pipe Pb (see FIG. 1). The outflow of lubricating oil is suppressed.

<< Third Embodiment >>
In the third embodiment, the notch portion 12d (second notch portion) and the rib 12e (second rib) are also provided in the lower portion of the balance weight 12D (see FIGS. 9A and 9B). Is different. The configuration of the upper and middle portions of the balance weight 12D is the same as that of the first embodiment (see FIG. 4). Therefore, a part different from the first embodiment will be described, and a description of the overlapping part will be omitted.

FIG. 9A is a perspective view of the balance weight 12D included in the compressor according to the third embodiment.
As shown in FIG. 9A, the balance weight 12D is provided with a notch 12d and a rib 12e at the lower part in the axial direction. That is, the balance weight 12D includes three notches 12d (second notch portions) provided on the outer peripheral edge portion on the opposite side (that is, the lower side) of the balance weight 12D to the rotor 7b. Each of the plurality of cutout portions 12d is provided in the circumferential direction of the balance weight 12D, and is open to the space G1 (see FIG. 1) in the closed container 1. Further, ribs 12e (second ribs) extending in the radial direction are provided between the notches 12d adjacent to each other in the circumferential direction.

Further, in the example of FIG. 9A, the position of the notch portion 12d when projected in the axial direction of the rotor 7b (see FIG. 1) substantially coincides with the position of another notch portion 12b above the notch portion 12d. There is. As a result, for example, when the balance weight 12D is made of laminated steel plates, the number of types of steel plates can be reduced, so that the manufacturing cost of the balance weight 12D can be reduced. Specifically, the first steel plate 121, the second steel plate 122, and the first steel plate are used by using the first steel plate 121 and the second steel plate 122 described in the second modification of the first embodiment (see FIG. 7). The balance weight 12D shown in FIG. 9A can be manufactured by laminating a predetermined number of 121 in this order in the axial direction.

FIG. 9B is a perspective view of the back side of the balance weight 12D included in the compressor.
That is, FIG. 9B is a perspective view of the balance weight 12D looking up obliquely from below. In the example of FIG. 9B, the lower surface of the balance weight 12D is flat, and the oil escape hole h3 and the rivet through hole h4 are opened.

<Effect>
According to the third embodiment, since the notch portion 12d and the rib 12e are provided in the lower portion of the balance weight 12D, when the balance weight 12D is rotating together with the rotor 7b (see FIG. 1), the upper notch portion is provided. In addition to the wall surface of 12b (see FIG. 9A), the wall surface of the lower notch 12d (see FIG. 9A) also collides with the mist-like lubricating oil. As a result, a lateral force is likely to be applied to the lubricating oil from the balance weight 12D, and the lubricating oil is less likely to move in the vertical direction. Therefore, since the flow in which the lubricating oil is blown up in the vertical direction is suppressed, the outflow of the lubricating oil through the discharge pipe Pb (see FIG. 1) can be suppressed.

<< Fourth Embodiment >>
The fourth embodiment is different from the first embodiment (see FIG. 4) in that the balance weight 12E (see FIG. 10) is cylindrical. One portion of the case where the cylindrical balance weight 12E (see FIG. 10) is cut on a predetermined plane K (see FIG. 10) parallel to the central axis Z of the rotor 7b is the first embodiment (FIG. 4). It has the same configuration as (see). Therefore, a part different from the first embodiment will be described, and a description of the overlapping part will be omitted.

FIG. 10 is a plan view of the balance weight 12E included in the compressor according to the fourth embodiment. That is, FIG. 10 is a plan view when the balance weight 12E is looked down from the rotor 7b side (see FIG. 1). Further, in FIG. 10, the region R when the permanent magnet 72b (see FIG. 1) of the rotor 7b is projected in the axial direction is shown by a broken line.

As shown in FIG. 10, the balance weight 12E has a cylindrical shape. The balance weight 12E includes recesses 12a,

notches

12b and 12f,

ribs

12c and 12g, oil escape holes h3, rivet through holes h4, and lightening holes h6.
As described above, one arcuate portion S1 when the cylindrical balance weight 12E is cut on a predetermined plane K parallel to the central axis Z of the rotor 7b is the same as that of the first embodiment (see FIG. 4). It has a similar configuration. Therefore, in the following, the other arcuate portion S2 will be mainly described, but one portion S1 may also be referred to.

In the example shown in FIG. 10, three notches 12b and three notches 12f recessed inward in the radial direction from the outer peripheral surface of the balance weight 12E are provided at substantially equal intervals in the circumferential direction. The three notches 12b are included in the arcuate portion S1, while the remaining three notches 12f are included in the arcuate portion S2. These

notches

12b and 12f are arranged so as to include a region R when the permanent magnet 72b is projected in the axial direction. As a result, even when the balance weight 12E is made of a magnetic material such as an iron material, the magnetic flux of the permanent magnet 72b of the rotor 7b (see FIG. 3) is moved to the balance weight 12E side via the end plate 72d (see FIG. 3). Leakage can be suppressed.

Further, ribs 12g extending in the radial direction are provided between the notches 12f adjacent to each other in the circumferential direction. By providing the ribs 12 g in this way, a lateral force is likely to act on the lubricating oil, and the ratio of the lateral velocity component to the magnitude of the velocity vector of the lubricating oil becomes large. Further, since the mist-like lubricating oil adheres to the balance weight 12E having a relatively large surface area, the amount of the mist-like lubricating oil floating on the lower side of the motor 7 (see FIG. 1) is reduced. Therefore, the amount of lubricating oil that rises through the gap between the stator 7a (see FIG. 1) and the rotor 7b (see FIG. 1) can be reduced.

A rivet through hole h4 is provided at a predetermined position of each rib 12 g. Further, the arc-shaped portion S1 included in the balance weight 12E is provided with three recesses 12a, while the other arc-shaped portion S2 is provided with a lightening hole h6. In the example of FIG. 10, the shape of the edge of the lightening hole h6 is the same as the shape of the edge of the recess 12a, but both may be different.

These three lightening holes h6 are provided in order to make the weight of the other portion S2 smaller than that of the one semicircular portion S1 (that is, the moments of inertia of the portions S1 and S2 are different). .. Each lightening hole h6 penetrates in the axial direction and opens on the rotor 7b side (see FIG. 1) of the balance weight 12E and also on the side opposite to the rotor 7b. Further, in order to reduce the weight of the other portion S2, the notch portion 12f between the ribs 12g adjacent to each other in the circumferential direction is provided over the entire length in the axial direction of the balance weight 12E.
The surface of the balance weight 12E opposite to the rotor 7b (see FIG. 1) may be flat or may be provided with a predetermined uneven shape.

<Effect>
While driving the motor 7 (see FIG. 1), the mist-like lubricating oil adheres to the balance weight 12E having a relatively large surface area, and a lateral force is applied to the mist-like lubricating oil from the wall surfaces of the

notches

12b and 12f. It works. As a result, the amount of lubricating oil that moves through the gap between the stator 7a (see FIG. 1) and the rotor 7b (see FIG. 1) is reduced, so that the amount of lubricating oil moves through the discharge pipe Pb (see FIG. 1). The outflow of lubricating oil can be suppressed.

Further, the

notches

12b and 12f are arranged so as to include the region R when the permanent magnet 72b is projected in the axial direction. Therefore, even when the balance weight 12E is made of a magnetic material such as an iron material, the magnetic flux of the permanent magnet 72b embedded in the rotor 7b (see FIG. 3) leaks through the end plate 72d (see FIG. 3). Can be suppressed.

<< Fifth Embodiment >>
In the fifth embodiment, the configuration of the air conditioner W (see FIG. 11) including the compressor 100 (see FIG. 11) will be described. Since the configuration of the compressor 100 is the same as that described in the first embodiment (see FIG. 1), the description thereof will be omitted.

FIG. 11 is a configuration diagram of the air conditioner W according to the fifth embodiment.
The solid line arrow in FIG. 11 indicates the flow of the refrigerant during the heating operation.
Further, 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 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 Fi. And have.

In the example shown in FIG. 11, the 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 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 exchange is performed between the refrigerant flowing 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 by driving the outdoor fan motor Mo, and is installed near 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 by driving the indoor fan motor Mi, and is installed in the vicinity of the indoor heat exchanger Ei.

The expansion valve Ve has a function of reducing 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. Devices such as the 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).

For example, during the cooling operation (see the broken arrow in FIG. 11), the compressor 100, the outdoor heat exchanger Eo (condenser), the expansion valve Ve, and the indoor heat exchanger Ei (evaporator) are sequentially passed through. Circulate.
On the other hand, during the heating operation (see the solid line arrow in FIG. 11), the compressor 100, the indoor heat exchanger Ei (condenser), the expansion valve Ve, and the outdoor heat exchanger Eo (evaporator) are sequentially passed through. , Refrigerant circulates. In this way, in the refrigerant circuit Q in which the refrigerant circulates in the refrigeration cycle via the compressor 100, the "condenser", the expansion valve Ve, and the "evaporator" in that order, the "condenser" and the "evaporator" One is the outdoor heat exchanger Eo and the other is the indoor heat exchanger Ei.

<Effect>
According to the fifth embodiment, by suppressing the outflow of the lubricating oil from the compressor 100, it is possible to provide the air conditioner W having high reliability and high operating efficiency.

≪Modification example≫
Although the compressor 100 and the like 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 configuration in which the balance weight 12 is provided on the lower side of the rotor 7b (see FIG. 1) has been described, but the present invention is not limited to this. That is, balance weights (not shown) may be provided on the upper side of the rotor 7b, or balance weights may be provided on both sides of the rotor 7b in the axial direction. Further, even if the balance weight 12 is provided on the side opposite to the discharge pipe Pb (see FIG. 1) in the axial direction of the rotor 7b and the balance weight (not shown) is not provided on the discharge pipe Pb side. Good.

Further, in each embodiment, the configuration in which the oil relief hole h3 provided in the recess 12a (see FIG. 4) penetrates the balance weight 12 in the axial direction has been described, but the present invention is not limited to this. That is, the oil accumulated in the recess 12a is released to the outside of the balance weight 12 by centrifugal force from the peripheral wall surface 122a (see FIG. 4) of the recess 12a through the oil relief hole (not shown) provided in the radial direction. It may be. That is, the balance weight 12 may have an oil escape hole (first hole) penetrating the rotor 7b from the recess 12a. In such a configuration, an oil escape hole (or a slit in the radial direction) may be provided so that the recess 12a and the notch 12b communicate with each other in the radial direction.

Further, in each embodiment, an example in which the balance weight 12 is made of an iron material has been described, but the present invention is not limited to this. For example, in addition to iron alloy and iron oxide, the balance weight 12 may be composed of a magnetic material such as ferrite or oxide. Further, the balance weight 12 may be composed of a non-magnetic material such as brass (brass) or stainless steel. Even in such a case, it is possible to prevent the lubricating oil from flowing out from the compressor 100 depending on the configuration of each embodiment.

Further, the shape and number of the recesses 12a and the notches 12b of the balance weight 12 are not limited to those described in each embodiment, and can be changed as appropriate. Further, the balance weight 12 may be configured by omitting the recess 12a and providing the balance weight 12 with a plurality of notches 12b. Even with such a configuration, the outflow of lubricating oil from the compressor 100 can be suppressed.

Further, in each embodiment, the configuration in which the region R (see FIG. 5A) on which the permanent magnet 72b of the rotor 7b (see FIG. 3) is projected in the axial direction is included in the notch portion 12b has been described, but the present invention is not limited to this. That is, the notch portion 12b may be arranged regardless of the position of the permanent magnet 72b.

Further, in the second embodiment (see FIG. 8A), in the balance weight 12C including the laminated steel plate, the first steel plate 121 is arranged at the upper end closest to the rotor 7b (see FIG. 1), while the rotor 7b is the most. The configuration in which the second steel plate 122 is arranged at the far lower end has been described, but the present invention is not limited to this. For example, the second steel plate 122 may be arranged at the upper end closest to the rotor 7b, or the first steel plate 121 may be arranged at the lower end farthest from the rotor 7b.

Further, in the second embodiment (see FIG. 8A), the balance weight 12C in which the first steel plate 121 and the second steel plate 122 are laminated one by one has been described, but a plurality of sheets may be laminated. That is, the balance weight 12C has a configuration in which at least one first steel plate 121 and at least one second steel plate 122 are alternately laminated in the axial direction of the rotor 7b (see FIG. 1). May be good.

Further, in the third embodiment (see FIG. 9A), the configuration in which the balance weight 12D includes the notch portion 12b (first notch portion) and the notch portion 12d (second notch portion) has been described, but one notch portion 12b is provided. It may be omitted.

In addition, each embodiment can be combined as appropriate. For example, the balance weight 12D may be made of a laminated steel plate by combining the second modification (see FIG. 7) and the third embodiment (see FIG. 9A) of the first embodiment.
Further, for example, by combining the first modification (see FIG. 6) and the second embodiment (see FIGS. 8A and 8B) of the first embodiment, the oil relief hole h3 of the balance weight 12C is formed on the rotor 7b. It may be provided on the side opposite to the direction of rotation.
Further, for example, the second embodiment (see FIG. 8A) and the fifth embodiment (see FIG. 11) may be combined so that the air conditioner W includes the compressor 100 having the balance weight 12C.

Further, in each embodiment, the scroll type compressor 100 (see FIG. 1) has been described, but the present invention is not limited to this. That is, the configuration of each embodiment can be applied to various types of compressors such as rotary type compressors.
Further, in each embodiment, the case where the compressor 100 is installed vertically has been described, but the present invention is not limited to this. That is, each embodiment can be applied even when the compressor 100 is arranged horizontally or diagonally.
Further, in each embodiment, the configuration in which the oil relief hole h3 is provided in the recess 12a of the balance weight 12 (see FIG. 4) has been described, but the oil relief hole h3 may be omitted. Further, the

adjacent recesses

12a and 12a may be communicated with each other in the circumferential direction. Further, the

adjacent notches

12b and 12b may be communicated with each other in the circumferential direction.

Further, the air conditioner W (see FIG. 11) described in the fifth 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, each embodiment can be applied to a refrigerating cycle device such as a refrigerator, a water heater, a hot water air conditioning system, and a refrigerator.

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 add / delete / replace a part of the configuration of each embodiment with another configuration.
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.

1 Closed container 2 Compression mechanism 4 Crankshaft (drive shaft)
7 Motor 7a Stator 7b Rotor 72b Permanent magnet (magnet)
12, 12A, 12B, 12C, 12D, 12E Balance weight 12a Recess 12b Notch (first notch)
12c rib (1st rib)
12d notch (second notch)
12e rib (second rib)
121 First steel plate (steel plate)
122 Second steel plate (steel plate)
100 Compressor Eo Outdoor Heat Exchanger (Condenser / Evaporator)
Ei Indoor Heat Exchanger (Evaporator / Condenser)
G1 space (space inside a closed container)
Ga space (space between the recess and the rotor)
Gb void h3 oil escape hole (first hole)
J Intermediate arc (set of points at intermediate positions of recesses)
R region (region when the magnet is projected in the axial direction of the rotor)
Q Refrigerant circuit Ve expansion valve W air conditioner

Claims

An electric motor with a stator and a rotor,
A drive shaft that rotates integrally with the rotor,
A compression mechanism that compresses the refrigerant as the drive shaft rotates,
An arc-shaped or cylindrical balance weight installed on the rotor,
The motor, the drive shaft, the compression mechanism, and a closed container containing at least the balance weight and containing lubricating oil are provided.
The balance weight has a plurality of notches recessed inward in the radial direction from the outer peripheral surface.
A compressor in which the plurality of notches are provided in the circumferential direction of the balance weight and are open to the space in the closed container.
The compressor according to claim 1, wherein the wall surface closest to the central axis of the rotor in each of the notches is located radially outside the inner peripheral surface of the balance weight.
The plurality of notches include a plurality of first notches provided on the outer peripheral edge of the balance weight on the rotor side.
The compressor according to claim 1, wherein a first rib extending in the radial direction is provided between the first notches adjacent to each other in the circumferential direction.
The balance weight has a recess formed in the axial direction of the rotor from the end face on the rotor side.
The recess is provided inside the notch in the radial direction.
The compressor according to claim 1, wherein the recess and the notch are arranged in the radial direction.
The balance weight has a recess formed in the axial direction of the rotor from the end face on the rotor side.
The compressor according to claim 1, wherein the end face of the balance weight on the rotor side is in contact with the rotor around the recess.
It has a first hole provided in the recess and penetrating the rotor from the recess.
The compressor according to claim 5, wherein the first hole opens in a space between the recess and the rotor and also in a space in the closed container.
The compressor according to claim 6, wherein the first hole is provided radially outside the intermediate position of the recess in the radial direction.
The compressor according to claim 6, wherein the first hole is provided in the recess on the side opposite to the direction in which the rotor rotates in the circumferential direction.
The end face of the first rib on the rotor side is in contact with the rotor.
The compressor according to claim 3, wherein the radial outer wall surface of the first rib is flush with the outer peripheral surface of the balance weight.
The balance weight has a plurality of steel plates laminated in the axial direction of the rotor, and has a plurality of steel plates.
The compression according to claim 1, wherein the plurality of the steel plates include at least a first steel plate provided with the notch portion and a second steel plate not provided with the notch portion. Machine.
10. The balance weight according to claim 10, wherein at least one of the first steel plates and at least one of the second steel plates are alternately laminated in the axial direction of the rotor. Compressor.
In the balance weight, the first steel plate is provided at a position closest to the rotor in the axial direction of the rotor.
The notch portion of the first steel plate at a position closest to the rotor in the axial direction includes a region when a magnet embedded in the rotor is projected in the axial direction. The compressor according to claim 10.
The plurality of notches further include a plurality of second notches provided on the outer peripheral edge of the balance weight opposite to the rotor.
The compressor according to claim 1, wherein a second rib extending in the radial direction is provided between the second notches adjacent to each other in the circumferential direction.
Includes a refrigerant circuit in which the refrigerant circulates sequentially through the compressor, condenser, expansion valve, and evaporator.
The compressor
An electric motor with a stator and a rotor,
A drive shaft that rotates integrally with the rotor,
A compression mechanism that compresses the refrigerant as the drive shaft rotates,
An arc-shaped or cylindrical balance weight installed on the rotor,
The motor, the drive shaft, the compression mechanism, and a closed container containing at least the balance weight and containing lubricating oil are provided.
The balance weight has a plurality of notches recessed inward in the radial direction from the outer peripheral surface.
An air conditioner in which the plurality of notches are provided in the circumferential direction of the balance weight and are open to the space in the closed container.