SCROLL COMPRESSOR

Abstract

A scroll compressor includes a hermetic container in which a refrigeration machine oil is stored in a bottom area, a compression mechanism that compresses a refrigerant which is suctioned into the hermetic container, an electric motor which has a motor rotor and a motor stator and is configured to drive the compression mechanism which is connected thereto via a shaft, a sub-frame that is fixed to the hermetic container and supports the shaft in a rotatable manner from a lower side of the electric motor, a balance weight that is disposed on a lower end face of the motor rotor, and a fixed cup that is disposed on an upper end of the sub-frame and surrounds the balance weight.

Description

TECHNICAL FIELD

The present invention relates to scroll compressors that reduce the amount of refrigerating machine oil discharged to the outside of a hermetic container.

BACKGROUND ART

In scroll compressors that use a compression mechanism which is driven by an electric motor element to compress a refrigerant which is introduced in a hermetic container, some scroll compressors reduce the amount of refrigerating machine oil discharged to the outside of the hermetic container (for example, see Patent Literatures 1 and 2).

In the scroll compressor described in Patent Literature 1, a compression element (2) is positioned on the lower part in a vertical hermetic casing (1) and a motor (3) with a drive shaft (4) is positioned on the upper side of the compression element (2). A bearing (15) of the drive shaft (4) is disposed on the upper side of the motor and an oil supply pump (8) is disposed on the lower side of the drive shaft (4). A forced oil supply passage (18) which communicates with the oil supply pump (8) is disposed to supply oil to the bearing (15) and a spiral groove (19) is formed on the outer peripheral surface of a rotor (31) of the motor (3) to downwardly return the oil supplied to the bearing (15) in a forcible manner such that the oil after lubrication can be returned to the oil supply pump without using a special oil separator while the oil is forcibly supplied to the bearing (15) disposed on the upper side.

Further, the scroll compressor described in Patent Literature 2 includes a scroll compression mechanism (11) that compresses a refrigerant and a drive motor (13) that is connected to the scroll compression mechanism (11) via a drive shaft (15) to drive the scroll compression mechanism (11), which are housed in a casing (3), and the scroll compression mechanism (11) is supported by a main frame (21) in the casing (3), the drive shaft (15) of the drive motor (13) is supported by a bearing plate (8) in the casing (3), the bearing plate (8) has an opening (8E) that communicates upper and lower spaces of the bearing plate (8) and includes a cover (80) that covers the surrounding of the drive shaft (15) between the drive motor (13) and the bearing plate (8), and the cover (80) includes a plurality of cover members (80A, 80B) which are separated into such sizes that are allowed to pass through the opening (8E).

CITATION LIST

Patent Literature

[Patent Literature 1] Japanese Unexamined Patent Application Publication No. 5-302581 (for example, see FIG. 1)

[Patent Literature 2] Japanese Unexamined Patent Application Publication No. 2013-47481 (for example, see FIG. 1)

SUMMARY OF INVENTION

Technical Problem

However, in conventional scroll compressors shown in Patent Literatures 1 and 2, a balance weight disposed on the lower end of the rotor of the electric motor may be rotated due to driving of the electric motor during start of operation. Then, when the liquid level of the refrigerating machine oil or the mixed liquid of the refrigerating machine oil and the refrigerant is around or above the lower end of the electric motor element, the refrigerating machine oil or the mixed liquid of the refrigerating machine oil and the refrigerant may be mixed by the balance weight. This causes a problem that the refrigerating machine oil is discharged to the outside of the hermetic container, which results in decreased reliability of the bearing, and the amount of oil in the refrigeration cycle increases, which results in decreased cycle efficiency.

The present invention has been made to solve the above problem and an object of the invention is to provide a scroll compressor that prevents a refrigerating machine oil or a mixed liquid of refrigerating machine oil and refrigerant from being mixed during driving period of an electric motor and reduces the amount of refrigerating machine oil discharged to the outside of a hermetic container.

Solution to Problem

A scroll compressor according to the present invention includes a hermetic container in which a refrigeration machine oil is stored in a bottom area, a compression mechanism that compresses a refrigerant which is suctioned into the hermetic container, an electric motor which has a motor rotor and a motor stator and is configured to drive the compression mechanism which is connected thereto via a shaft, a sub-frame that is fixed to the hermetic container and supports the shaft in a rotatable manner from a lower side of the electric motor, a balance weight that is disposed on a lower end face of the motor rotor, and a fixed cup that is disposed on an upper end of the sub-frame and surrounds the balance weight.

Advantageous Effects of Invention

According to the scroll compressor of the present invention, the fixed cup is not rotated even during driving period of the electric motor since the fixed cup is disposed on the upper end of the sub-frame which is fixed to the hermetic container. Further, the balance weight is surrounded by the fixed cup.

Accordingly, the refrigerating machine oil or the mixed liquid of the refrigerating machine oil and the refrigerant can be prevented from being mixed by rotation of the balance weight, the amount of the refrigerating machine oil discharged to the outside of the hermetic container can be reduced, the reliability of the bearings is improved, and the cycle efficiency of the refrigeration cycle is improved.

BRIEF DESCRIPTION OF DRAWINGS

FIG. 1 is a vertical cross-sectional view of a scroll compressor according to Embodiment 1 of the present invention.

FIG. 2 is an enlarged view of an essential part of FIG. 1.

FIG. 3 is a transverse cross-sectional view of a guide frame taken along the line A-A of FIG. 1.

FIG. 4 is a transverse cross-sectional view of a motor stator taken along the line B-B of FIG. 1.

FIG. 5 is a vertical cross-sectional view of a fixed cup according to Embodiment 3 of the present invention.

FIG. 6A is a vertical cross-sectional view which shows a penetrating flow passage of a motor rotor according to Embodiment 5 of the present invention.

FIG. 6B is a transverse cross-sectional view which shows a penetrating flow passage of a motor rotor according to Embodiment 5 of the present invention.

FIG. 7 is a view which shows a relationship of a vertical cross-sectional area of a gap space of the scroll compressor and a circulation amount of a refrigerating machine oil according to Embodiment 5 of the present invention.

DESCRIPTION OF EMBODIMENTS

Embodiments of the invention will be described below with reference to the drawings. It should be noted that the present invention is not limited by the following Embodiments. In the accompanying drawings, the size relationship between components may be different from the actual relationship.

Embodiment 1

FIG. 1 is a vertical cross-sectional view of a scroll compressor 100 according to Embodiment 1 of the present invention, and FIG. 2 is an enlarged view of an essential part of FIG. 1.

The scroll compressor 100 according to Embodiment 1 of the present invention includes a compression mechanism 14 which has a fixed scroll 1 and a rocking scroll 2 in a hermetic container 10 which is in the shape of a hermetic dome and is configured to compress a refrigerant, and an electric motor 5 which has a motor rotor 5a and a motor stator 5b and is configured to drive the compression mechanism 14 which is connected to the electric motor 5 via a main shaft 6.

The fixed scroll 1 is composed of a base plate 1a and a scroll lap 1b, and an outer periphery of the fixed scroll 1 is fastened to a guide frame 4 by using a bolt (not shown in the figure). The scroll lap 1b is disposed on one side (the lower side in FIG. 1) of the base plate 1a, and oldham guiding grooves 1c are formed on the outer periphery of the fixed scroll 1 at two positions which are substantially on a straight line. Further, a fixed key 9a of an oldham mechanism 9 engages the oldham guiding groove 1c in a reciprocatingly slidable manner. Still further, a discharge port 1d is formed at the center of the base plate 1a through which a refrigerant is discharged. In addition, a suction pipe 13 is press fit into the fixed scroll 1 through the hermetic container 10 with a suction port 1e being located inside the fixed scroll 1.

The rocking scroll 2 is composed of a base plate 2a and a scroll lap 2b. The scroll lap 2b which has a shape substantially the same as that of the scroll lap 1b of the fixed scroll 1 is disposed on one side (the upper side in FIG. 1) of the base plate 2a. The scroll lap 1b of the fixed scroll 1 and the scroll lap 2b of the rocking scroll 2 geometrically form a compression chamber 1f. The refrigerant suctioned into the hermetic container 10 is compressed in response to change in volume of the compression chamber 1f. Further, a boss 2d in a hollow cylindrical shape is formed at the center of a surface (the lower side in FIG. 1, which is hereinafter referred to as the lower surface) of the base plate 2a opposite to a surface on which the scroll lap 2b is disposed. The boss 2d rotatably supports a rocking shaft section 6a on the upper end of the main shaft 6. In addition, a thrust surface 2f is formed around the circumference of the boss 2d to be in sliding contact with the thrust bearing 3a of a compliant frame 3.

Oldham guiding grooves 2c which has a phase difference of 90 degrees from the oldham guiding grooves 1c of the fixed scroll 1 are formed on the outer periphery of the base plate 2a of the rocking scroll 2 at two positions which are substantially on a straight line. Further, a rocking key 9b of the oldham mechanism 9 engages the oldham guiding groove 2c in a reciprocatingly slidable manner. In addition, a rocking scroll bleeding hole 2g which penetrates the compression chamber 1f and the thrust surface 2f is formed on the base plate 2a so that a refrigerant gas is extracted during compression through the bleeding hole 2g and is guided to the thrust surface 2f.

The compliant frame 3 is provided with upper and lower cylindrical surfaces 3p, 3s formed on the outer periphery of the compliant frame 3 which are radially supported by cylindrical surfaces 4c, 4d formed on the inner periphery of the guide frame 4. The compliant frame 3 is also provided with a main shaft bearing 3c and an auxiliary main shaft bearing 3d at the center of the compliant frame 3 such that the main shaft bearing 3c and the auxiliary main shaft bearing 3d radially support the main shaft 6 which is rotated by the electric motor 5. Further, a communication hole 3e is formed to penetrate the thrust bearing 3a in the axis direction, and the opening 3t of the thrust bearing 3a is located at a position which faces the rocking scroll bleeding hole 2g.

A slide surface 3b on which an oldham mechanism annular section 9c reciprocatingly slides is formed outside the thrust bearing 3a of the compliant frame 3, and a communication hole 3f that communicates a base plate circumferential space 2k and a frame upper space 4a is provided so as to communicate with the inside of the oldham mechanism annular section 9c. Further, the compliant frame 3 is provided with an intermediate pressure regulating valve 3g that adjusts a pressure of a boss outer diameter space 2n and an intermediate pressure regulating valve guard 3h. Further, an intermediate pressure regulating valve space 3n is formed to house an intermediate pressure regulating valve spring 3k. The intermediate pressure regulating valve spring 3k is housed in a collapsed state which is shorter than its natural length.

FIG. 3 is a transverse cross-sectional view of the guide frame 4 taken along the line A-A of FIG. 1.

As shown in FIG. 3, the outer peripheral surface of the guide frame 4 is fixed to the hermetic container 10 by shrink-fitting, welding or the like, and first notches 4f are formed on the outer periphery to serve as passages for a mixed gas of the refrigerant and the refrigerating machine oil. Further, as shown in FIG. 1, the first notches 4f are formed at positions on the opposite side of the discharge pipe 12. A first discharge passage 4g is formed to extend from the center on the lower end of the guide frame 4 to the side face, and the discharge pipe 12 is disposed to penetrate the hermetic container 10 with the end portion 12a being housed in the first discharge passage 4g. A cover 16 which has an opening 4h and forms a second discharge passage 16a and an opening 16b is disposed on one side (the lower side in FIG. 1) of the guide frame 4.

A frame lower space 4b is formed by the inner surface of the guide frame 4 and the outer surface of the compliant frame 3, and the upper side and the lower side of the frame lower space 4b are partitioned by an upper ring seal member 7a and a lower ring seal member 7b, respectively. Although ring-shaped seal grooves are formed at two positions on the inner peripheral surface of the guide frame 4 to house the upper ring seal member 7a and the lower ring seal member 7b, the seal groove may be formed on the outer peripheral surface of the compliant frame 3. The frame lower space 4b communicates only with the communication hole 3e of the compliant frame 3 and is configured to seal the refrigerant gas during compression which is supplied through the rocking scroll bleeding hole 2g. Further, a space around the circumference of the thrust bearing 3a, which is surrounded by the base plate 2a of the rocking scroll 2 and the compliant frame 3 on its upper and lower sides, that is, a base plate circumferential space 2k is a lower pressure space of a suction gas atmosphere (suction pressure).

The motor rotor 5a is disposed inside the motor stator 5b, and the penetrating flow passage 5f is formed in the motor rotor 5a in the axis direction. The motor stator 5b is disposed outside the motor rotor 5a, and a motor stator coil 5c is wound around the motor stator 5b. A main shaft portion 6b of the main shaft 6 is fixedly provided inside the motor rotor 5a. The motor rotor 5a rotates to cause the main shaft 6 to rotate and transmits a drive force to the compression mechanism 14 which is connected via the main shaft 6. Further, second notches 5g are formed between the outer periphery of the motor stator 5b and the hermetic container 10 to serve as passages for a mixed gas of the refrigerant and the refrigerating machine oil.

A rocking shaft portion 6a which is rotatably supported by the rocking bearing 2e of the rocking scroll 2 is formed on the upper end of the main shaft 6, and a main shaft balance weight 6f is shrink-fitted under the rocking shaft portion 6a. Further, the main shaft portion 6b which is rotatably supported by the main shaft bearing 3d and the auxiliary main shaft bearing 3d of the compliant frame 3 is formed under the main shaft balance weight 6f. Still further, a sub-shaft portion 6c which is rotatably supported by a sub-shaft bearing 8e of the sub-frame 8 is formed on the lower end of the main shaft 6, and the outer peripheral surface of the sub-frame 8 is fixed to the hermetic container 10 by shrink-fitting, welding or the like. The motor rotor 5a is shrink-fitted between the sub-shaft portion 6c and the main shaft portion 6b. The refrigerating machine oil is stored in an oil sump 11 at the bottom of the hermetic container 10, and the refrigerating machine oil is suctioned through an oil supply port 6d which is formed on the lower end face of the main shaft 6 by using an oil supply mechanism disposed in the main shaft 6.

An upper balance weight 15a and a lower balance weight 15b is fixed to the upper end face and the lower end face of the motor rotor 5a, respectively, and in addition to the main shaft balance weight 6f, those balance weights disposed at three positions keep the static balance and the dynamic balance. That is, those balance weights keep balance during shut down period of the electric motor 5 and offset the imbalance between the centrifugal force and the moment generated at the compression mechanism 14 during driving period of the electric motor 5 to keep balance. Further, an upper cup 17 is disposed to surround the upper balance weight 15a at the upper end of the motor rotor 5a, and a fixed cup 18 is disposed to surround the lower balance weight 15b at the upper end of the sub-frame 8. The fixed cup 18 is formed to separate a cup inside space 18e which contains the lower balance weight 15b therein and a cup outside space 18f which does not contain the lower balance weight 15b therein (which is located outside the fixed cup 18) in the space between the upper end of the sub-frame 8 and the lower balance weight 15b. Further, as shown in FIG. 2, a gap space 18d is formed between the upper end of the fixed cup 18 and the lower end of the motor rotor 5a.

FIG. 4 is a transverse cross-sectional view of the motor stator 5b taken along the line B-B of FIG. 1.

As shown in FIG. 4, the outer peripheral surface of the motor stator 5b is fixed to the hermetic container 10 by shrink-fitting, welding or the like, and the second notches 5g are formed on the outer periphery to serve as passages for a mixed gas of the refrigerant and the refrigerating machine oil. Further, as shown in FIG. 1, glass terminals 10a are disposed on the side face of the hermetic container 10, and the lead wires 5h which extend from the motor stator 5b are connected to the glass terminals 10a.

Next, an operation of the scroll compressor 100 according to Embodiment 1 during operating period will be described.

The suction refrigerant is suctioned through the suction pipe 13 during starting and operating period of the scroll compressor 100 and enters the compression chamber 1f formed by the scroll lap 1b of the fixed scroll 1 and the scroll lap 2b of the rocking scroll 2. The rocking scroll 2 which is driven by the electric motor 5 reduces the volume of the compression chamber 1f as the eccentric rotation movement. This compression stroke causes the suction refrigerant to be under high pressure. Further, in this compression stroke, the refrigerant gas of the intermediate pressure during compression is guided from the rocking scroll bleeding hole 2g of the rocking scroll 2 to the frame lower space 4b via the communication hole 3e of the compliant frame 3 so as to keep the intermediate pressure atmosphere of the frame lower space 4b.

After the compression stroke, the mixed gas of the refrigerant and the refrigerating machine oil which is suctioned from the suction hole 1 e and is discharged from the discharge port 1d of the fixed scroll 1 is guided to the bottom of the hermetic container 10 through the first notches 4f formed on the outer periphery of the guide frame 4 and the second notches 5g formed on the outer periphery of the motor stator 5b. The mixed gas of the refrigerant and the refrigerating machine oil are separated in the course of being guided to the bottom of the hermetic container 10. The separated refrigerant gas flows through the gap space 18d between the upper end of the fixed cup 18 and the lower end of the motor rotor 5a and the penetrating flow passage 5f of the motor rotor 5a and is released to the outside of the hermetic container 10 through the discharge pipe 12.

Next, a state of the scroll compressor 100 according to Embodiment 1 during shut down period will be described.

In the shut down period of the scroll compressor 100, when the temperature of the scroll compressor 100 is low, the refrigerant in the refrigeration cycle is liquefied and flows into the scroll compressor 100 and is mixed with the refrigerating machine oil. The liquid level of the mixed liquid comes near the lower end of the motor stator coil 5c which is wound around the motor stator 5b or above the lower end of the motor stator coil 5c.

Next, an operation of the scroll compressor 100 according to Embodiment 1 during start of operation will be described.

Since the fixed cup 18 is disposed on the upper end of the sub-frame 8, the fixed cup 18 does not rotate even during driving period of the electric motor 5. Further, the lower balance weight 15b is surrounded by the fixed cup 18. Accordingly, the refrigerating machine oil or the mixed liquid of the refrigerating machine oil and the refrigerant can be prevented from being mixed by rotation of the lower balance weight 15b, the amount of the refrigerating machine oil discharged to the outside of the hermetic container can be reduced, the reliability of all the bearings (rocking bearing 2e, thrust bearing 3a, main shaft bearing 3c, auxiliary main shaft bearing 3d, sub-shaft bearing 8a) is improved, and the cycle efficiency of the refrigeration cycle is improved.

The refrigerating machine oil may be miscible or immiscible with the refrigerant. In the case of the refrigerating machine oil miscible with the refrigerant, the refrigerating machine oil released into the refrigeration cycle is returned to the scroll compressor 100 along with the refrigerant flowing from the refrigeration cycle during shut down period of the scroll compressor 100. As a result, the liquid level of the mixed liquid becomes higher than that of the immiscible refrigerating machine oil. Accordingly, the fixed cup 18 is more effective when used for the miscible refrigerating machine oil.

Embodiment 2

Next, the scroll compressor according to Embodiment 2 will be described. In Embodiment 2, the refrigerating machine oil is sealed in the scroll compressor with the liquid level being above the lower end of the motor stator coil 5c which is wound around the motor stator 5b.

In the following description, the configuration and operation which are the same as those of Embodiment 1 will not be described.

When the scroll compressor is installed in air conditioning apparatuses or refrigerating machines which include a large refrigeration cycle, the amount of refrigerating machine oil sealed in the scroll compressor is increased in accordance with the increased amount of refrigerant in the refrigeration cycle so that the liquid level of the refrigerating machine oil is above the lower end of the electric motor 5.

As described above, even when the refrigerating machine oil is sealed with the liquid level thereof being above the lower end of the electric motor 5, the refrigerating machine oil or the mixed liquid of the refrigerating machine oil and the refrigerant can be prevented from being mixed by rotation of the lower balance weight 15b, the amount of the refrigerating machine oil discharged to the outside of the hermetic container can be reduced, the reliability of all the bearings is improved, and the cycle efficiency of the refrigeration cycle is improved, since the lower balance weight 15b is surrounded by the fixed cup 18 disposed on the upper end of the sub-frame 8.

Embodiment 3

Next, the scroll compressor according to Embodiment 3 will be described. In Embodiment 3, the fixed cup 18 is formed of two parts in the scroll compressor.

In the following description, the configuration and operation which are the same as those of Embodiment 1 or 2 will not be described.

FIG. 5 is a vertical cross-sectional view of the fixed cup 18 according to Embodiment 3 of the present invention.

As shown in FIG. 5, the fixed cup 18 is composed of a seat member 18b for fixing to the sub-frame 8 and a cup member 18a that surrounds the lower balance weight 15b, and the cup member 18a is connected to the seat member 18b via a connection section 18c.

As described above, since the fixed cup 18 is composed of two members of the seat member 18b and the cup member 18a, the seat member 18b can be formed thick to retain the fixture strength and the cup member 18a can be formed thin to save material cost.

Embodiment 4

Next, the scroll compressor according to Embodiment 4 will be described. In Embodiment 4, the seat member 18b and the cup member 18a are welded in the scroll compressor.

In the following description, the configuration and operation which are the same as those of any of Embodiments 1 to 3 will not be described.

In FIG. 5, the cup member 18a is connected to the seat member 18b by welding at a connection section 18c.

As described above, since the seat member 18b and the cup member 18a are connected by welding in the fixed cup 18, it is possible to prevent the cup member 18a from being detached from the seat member 18b due to pressure difference between the sup inside space 18e and the cup outside space 18f.

Embodiment 5

Next, the scroll compressor according to Embodiment 5 will be described. In Embodiment 5, dimensions between the motor rotor 5a and the fixed cup 18 in the scroll compressor are defined.

In the following description, the configuration and operation which are the same as those of any of Embodiments 1 to 4 will not be described.

FIG. 6A is a vertical cross-sectional view which shows the penetrating flow passage 5f of the motor rotor 5a according to Embodiment 5 of the present invention. FIG. 6B is a transverse cross-sectional view which shows the penetrating flow passage 5f of the motor rotor 5a according to Embodiment 5 of the present invention.

In the scroll compressor according to Embodiment 5 of the present invention, dimensions of the fixed cup 18 are defined such that the vertical cross-sectional area of the gap space 18d between the upper end of the fixed cup 18 shown in FIG. 2 and the lower end of the motor rotor 5a is larger than the vertical cross-sectional area of the penetrating flow passage 5f of the motor rotor 5a shown in FIGS. 6A, 6B and 7.

FIG. 7 is a view which shows a relationship of a vertical cross-sectional area of the gap space of the scroll compressor and a circulation amount of the refrigerating machine oil according to Embodiment 5 of the present invention. In FIG. 7, the horizontal axis represents the vertical cross-sectional area of the gap space 18d, and the vertical axis represents the circulation amount of the refrigerating machine oil in the refrigeration cycle during operating period of the scroll compressor. The dotted line represents the position of the vertical cross-sectional area of the penetrating flow passage 5f of the motor rotor 5a in FIG. 7.

As shown in FIG. 7, when the vertical cross-sectional area of the gap space 18d becomes larger than the the vertical cross-sectional area of the penetrating flow passage 5f of the motor rotor 5a, the circulation amount of the refrigerating machine oil during operating period of the scroll compressor decreases. Based on this relationship, the amount of the refrigerating machine oil released from the scroll compressor into the refrigeration cycle during operating period can be reduced by defining a height dimension or a diameter dimension of the fixed cup 18 such that the vertical cross-sectional area of the gap space 18d is larger than the the vertical cross-sectional area of the penetrating flow passage 5f of the motor rotor 5a. Accordingly, the reliability of all the bearings is improved, and the cycle efficiency of the refrigeration cycle is improved.

[Reference Signs List]

1 fixed scroll; 1a base plate (of the fixed scroll); 1b scroll lap (of the fixed scroll); 1c oldham guiding groove (of the fixed scroll); 1d discharge port; 1e suction port; 1f compression chamber 2 rocking scroll; 2a base plate (of the rocking scroll); 2b scroll lap (of the rocking scroll); 2c oldham guiding groove (of the rocking scroll); 2d boss; 2e rocking bearing; 2f thrust surface; 2g rocking scroll air bleed hole; 2k base plate circumferential space; 2n boss outer diameter space; 3 compliant frame; 3a thrust bearing; 3b slide surface; 3c main shaft bearing; 3d auxiliary main shaft bearing; 3e communication hole; 3f communication hole; 3g intermediate pressure regulating valve; 3h intermediate pressure regulating valve guard; 3k intermediate pressure regulating spring; 3n intermediate pressure regulating valve space; 3p cylindrical surface (of the compliant frame); 3t thrust bearing opening; 4 guide frame; 4a frame upper space; 4b frame lower space; 4c cylindrical surface (of the guide frame); 4f first notch; 4g first discharge passage; 4h opening; 5 electric motor; 5a motor rotor; 5b motor stator; 5c motor stator coil; 5f penetrating flow passage; 5g second notch; 5h lead wire; 6 main shaft; 6a rocking shaft portion; 6b main shaft portion; 6c sub-shaft portion; 6d oil supply port; 6f main shaft balance weight; 7a upper ring seal member; 7b upper ring seal member; 8 sub-frame; 8a sub-shaft bearing; 9 oldham mechanism; 9a fixed key of the oldham mechanism; 9b rocking key of the oldham mechanism; 9c oldham mechanism annular section; 10 hermetic container; 10a glass terminal; 11 oil sump; 12 discharge pipe; 12a end portion (of the discharge pipe); 13 suction pipe; 14 compression mechanism; 15 balance weight; 15a upper balance weight; 15b lower balance weight; 16 cover; 16a second discharge passage; 16b opening; 17 upper cup; 18 fixed cup; 18a cup member; 18b seat member; 18c connection section; 18d gap space; 18e cup inside space; 18f cup outside space; 100 scroll compressor

Claims

1. A scroll compressor comprising:

a hermetic container in which a refrigeration machine oil is stored in a bottom area of the hermetic container;

a compression mechanism that compresses a refrigerant which is suctioned into the hermetic container;

an electric motor which has a motor rotor and a motor stator and is configured to drive the compression mechanism which is connected to the electric motor via a shaft;

a sub-frame that is fixed to the hermetic container and supports the shaft in a rotatable manner from a lower side of the electric motor;

a balance weight that is disposed on a lower end face of the motor rotor; and

a fixed cup that is disposed on an upper end of the sub-frame and surrounds the balance weight.

2. The scroll compressor of claim 1, wherein the fixed cup separates an inside space which contains the balance weight therein and an outside space which does not contain the balance weight therein in a space between the upper end of the sub-frame and the balance weight.

3. The scroll compressor of claim 1, wherein the refrigerating machine oil is sealed with the liquid level thereof being above the lower end of the electric motor.

4. The scroll compressor of claim 2, wherein the refrigerating machine oil is sealed with the liquid level thereof being above the lower end of the electric motor.

5. The scroll compressor of claim 1, wherein the fixed cup is formed by connecting a seat member for fixing to the sub-frame and a cup member that surrounds the balance weight.

6. The scroll compressor of claim 2, wherein the fixed cup is formed by connecting a seat member for fixing to the sub-frame and a cup member that surrounds the balance weight.

7. The scroll compressor of claim 3, wherein the fixed cup is formed by connecting a seat member for fixing to the sub-frame and a cup member that surrounds the balance weight.

8. The scroll compressor of claim 4, wherein the fixed cup is formed by connecting a seat member for fixing to the sub-frame and a cup member that surrounds the balance weight.

9. The scroll compressor of claim 5, wherein the seat member for fixing to the sub-frame and the cup member that surrounds the balance weight are connected by welding.

10. The scroll compressor of claim 6, wherein the seat member for fixing to the sub-frame and the cup member that surrounds the balance weight are connected by welding.

11. The scroll compressor of claim 7, wherein the seat member for fixing to the sub-frame and the cup member that surrounds the balance weight are connected by welding.

12. The scroll compressor of claim 8, wherein the seat member for fixing to the sub-frame and the cup member that surrounds the balance weight are connected by welding.

13. The scroll compressor of claim 1, wherein a penetrating flow passage is formed in the motor rotor in an axis direction, and a vertical cross-sectional area of a gap space between an upper end of the fixed cup and a lower end of the motor rotor is larger than the vertical cross-sectional area of the penetrating flow passage.