KR20200087836A - Rotary compressor - Google Patents

Abstract

The rotary compressor includes an electric motor portion and a compressor mechanism portion for compressing a refrigerant by a driving force transmitted from the electric motor portion in a sealed container. The compressor mechanism includes a crank shaft that is rotationally driven by an electric motor unit, a cylinder having a cylinder chamber, a shaft support for closing the cylinder chamber, a rolling piston that eccentrically rotates with the eccentric shaft portion to compress refrigerant, and a cylinder chamber and a suction chamber. It has a vane partitioned by a compression chamber, and a vane spring that presses the tip of the vane against the outer circumferential surface of the rolling piston. In the cylinder, a vane spring groove for extending the vane spring storage hole is formed around the vane groove from the vane spring storage hole toward the cylinder chamber.

Description

Rotary compressor

The present invention relates to a rotary compressor used in a cold-heating device such as an air conditioner.

The rotary compressor, for example, as disclosed in Patent Document 1, includes an electric motor unit and a compressor mechanism driven by the electric motor unit in a sealed container. The compression mechanism portion is provided in a vane groove formed in the radial direction of the cylinder, and has a vane that divides the cylinder chamber of the cylinder into a suction chamber and a compression chamber. In addition, the compression mechanism portion is accommodated in a cylinder chamber, a rolling piston compressing refrigerant by eccentric rotation, and a vane spring housed in a vane spring storage hole formed in the cylinder and forcing the tip of the vane to press firmly against the outer circumferential surface of the rolling piston. Have

Japanese Patent Publication No. 11-022675

Generally, in a rotary compressor, it is effective to improve reliability by forming a vane groove for a long time, widening a sliding area between the vane and the vane groove, and stabilizing the sliding state of the vane and the vane groove. However, in order to add the vane with the vane spring and follow the rolling piston, it is necessary to sufficiently secure the length of the vane spring storage hole. Therefore, in the rotary compressor, when the vane groove is lengthened, the hermetic container is expanded as much, and the entire apparatus becomes large.

The present invention has been made to solve the above-described problems, and an object of the present invention is to provide a rotary compressor capable of improving reliability by increasing a sliding area between the vane and the vane groove without expanding the sealed container. Is done.

The rotary compressor according to the present invention includes an electric motor unit and a compressor mechanism for compressing refrigerant by a driving force transmitted from the electric motor unit, in the sealed container, wherein the compressor mechanism has an eccentric shaft, and the electric motor unit A crank shaft that is rotationally driven, a cylinder fixed to the hermetic container, a cylinder having a cylinder chamber, provided on both end surfaces of the cylinder, a shaft support for closing the cylinder chamber, and fitted to the eccentric shaft portion, It is accommodated in the cylinder chamber, and a rolling piston for compressing the refrigerant by eccentric rotation with the eccentric shaft portion, a vane provided in the vane groove formed in the radial direction of the cylinder, and a vane partitioning the cylinder chamber into a suction chamber and a compression chamber, and the cylinder A vane spring groove that is accommodated in the formed vane spring storage hole and biases the front end of the vane to press against the outer circumferential surface of the rolling piston. The cylinder includes a vane spring groove extending the vane spring storage hole, the vane groove. Around is formed from the vane spring receiving hole toward the cylinder chamber.

According to the rotary compressor according to the present invention, even if the length of the vane spring receiving hole is shortened, the vane can be added to the vane spring accommodated in the vane spring groove, so that it can follow the rolling piston. Therefore, in the rotary compressor, since the vane groove can be formed to be long as long as the length of the vane spring storage hole is shortened, the sliding area between the vane and the vane groove can be widened, and reliability can be improved.

1 is a longitudinal sectional view schematically showing the overall structure of a rotary compressor according to Embodiment 1 of the present invention.
2 is a cross-sectional view showing a main part of a compressor mechanism portion of a rotary compressor according to Embodiment 1 of the present invention.
3 is a cross-sectional view showing a cylinder of a rotary compressor according to Embodiment 1 of the present invention.
FIG. 4 is a cross-sectional view taken along line AA of FIG. 3;
5 is a modification of the rotary compressor according to Embodiment 1 of the present invention, and is a cross-sectional view showing the main part of the compressor mechanism.
Figure 6 is a cross-sectional view showing only the cylinder of the compression mechanism shown in Figure 5
7 is a cross-sectional view showing a cylinder of a rotary compressor according to Embodiment 2 of the present invention.
8 is a cross-sectional view showing a main part of a compression mechanism portion of a rotary compressor according to Embodiment 3 of the present invention.
9 is a cross-sectional view showing only the cylinder of the compression mechanism shown in FIG. 8;

EMBODIMENT OF THE INVENTION Hereinafter, embodiment of this invention is described with reference to drawings. In addition, in each figure, the same code|symbol is attached|subjected to the same or equivalent part, and the description is abbreviate|omitted or simplified suitably. In addition, regarding the structure described in each drawing, its shape, size, and arrangement can be appropriately changed within the scope of the present invention.

Embodiment 1.

First, the rotary compressor according to Embodiment 1 of the present invention will be described based on Figs. 1 is a longitudinal sectional view schematically showing the overall structure of a rotary compressor according to Embodiment 1 of the present invention. 2 is a cross-sectional view showing a main part of a compression mechanism portion of a rotary compressor according to Embodiment 1 of the present invention. 3 is a cross-sectional view showing a cylinder of a rotary compressor according to Embodiment 1 of the present invention. FIG. 4 is a cross-sectional view taken along line A-A shown in FIG. 3.

The rotary compressor 100 according to the first embodiment, as shown in FIG. 1, is a refrigerant in the interior of the hermetic container 1 by the electric motor part 2 and the driving force transmitted from the electric motor part 2. It is a configuration having a compression mechanism (3) for compressing. The electric motor part 2 and the compressor mechanism part 3 are connected via the crankshaft 4. In addition, the refrigerant is an R410 refrigerant as an example.

The sealed container 1 is connected to the accumulator 12 through the suction pipe 10, and refrigerant gas is received from the accumulator 12. The accumulator 12 is provided to separate the refrigerant into a liquid refrigerant and a gas refrigerant, so that the liquid refrigerant is not sucked into the compressor mechanism 3 as much as possible. In addition, a discharge pipe 11 through which compressed refrigerant is discharged is connected to an upper portion of the sealed container 1. Refrigerator oil (not shown) is stored at the bottom of the sealed container 1. The refrigerating machine oil mainly lubricates the sliding portion of the compressor mechanism (3).

The electric motor part 2 includes an annular stator 20 fixedly supported by a shrink fit or the like on the inner wall surface of the sealed container 1, and a rotor provided rotatably opposite the inner surface of the stator 20 ( 21). The crankshaft 4 is fitted into the rotor 21. The electric motor unit 2 is supplied with electric power through an airtight terminal (not shown) from the outside to drive.

As shown in Fig. 1 and Fig. 2, the compression mechanism 3 is provided with a crankshaft 4 that is rotationally driven by the electric motor 2, a cylinder 5 having a cylinder chamber 50, and a cylinder chamber. It is provided with an upper shaft 51 and a lower shaft 52, a rolling piston 6, and a vane 7 as the shaft support for closing the 50.

The crankshaft 4 has a main shaft part 40 fixed to the rotor 21 of the electric motor part 2, a sub shaft part 41 fitted with a cylinder 5 and provided on the opposite side of the main shaft part 40. , Has an eccentric shaft portion 42 provided between the main shaft portion 40 and the auxiliary shaft portion 41. An oil suction hole is formed in the shaft center portion of the crankshaft 4. The crankshaft 4 is provided with a helical centrifugal pump in the oil suction hole, and pumps up the refrigerated oil stored at the bottom of the hermetic container 1, so that it can be supplied to the sliding portion of the compression mechanism portion 3. .

The outer peripheral part of the cylinder 5 is fixed to the sealed container 1 by bolts or the like. As shown in Fig. 2, the cylinder 5 has an outer periphery formed in a circular shape, and a cylinder chamber 50, which is a circular space, is formed inside. The cylinder chamber 50 forms a compression chamber that compresses the refrigerant during driving. As shown in Fig. 1, the cylinder chamber 50 has both ends in the axial direction of the crankshaft 4 open, and the upper shaft support 51 and the cylinder 5 provided on the upper surface of the cylinder 5 are provided. It is occluded by the lower bearing 52 provided on the lower surface. In addition, the cylinder 5 is provided with a suction port (not shown) through which the refrigerant gas from the suction pipe 10 passes through the cylinder chamber 50 from the outer circumferential surface.

The upper shaft 51 is slidably fitted to the main shaft portion 40 of the crankshaft 4, so that one end face of the cylinder chamber 50 of the cylinder 5 (motor side 2) To occlude. On the other hand, the lower shaft receiving 52 slides freely on the sub-shaft portion 41 of the crankshaft 4, and occludes the other end surface (refrigerator side) of the cylinder chamber 50. Further, although not shown, the upper shaft 51 is provided with a discharge hole through which the refrigerant compressed in the compression chamber is discharged. In addition, a discharge muffler is attached to the upper shaft 51 to cover the discharge hole.

The rolling piston 6 is configured in a ring shape and slides freely on the eccentric shaft portion 42 of the crankshaft 4. The rolling piston 6 is provided in the cylinder chamber 50 together with the eccentric shaft portion 42, and eccentrically rotates with the eccentric shaft portion 42 in the cylinder chamber 50 to compress the refrigerant.

2, a vane groove 70 extending in the radial direction is formed in communication with the cylinder chamber 50, as shown in FIG. The vane groove 70 is provided with a vane 7 that divides the cylinder chamber 50 into a suction chamber and a compression chamber, and slides freely. During the compression process, the vane 7 reciprocates and slides the inside of the vane groove 70 following the eccentric rotation of the rolling piston 6 while the distal end abuts against the outer circumference of the rolling piston 6. The cylinder chamber 50 is divided into a suction chamber and a compression chamber by the front end of the vane 7 contacting the outer circumference of the rolling piston 6. The vane 7 is made of, for example, a nonmagnetic material.

2, the vane spring receiving hole 80 is formed in the cylinder 5 on the back side of the vane groove 70, as shown in FIG. The inner diameter of the vane spring storage hole 80 is formed to be larger than that of the vane groove 70. In the vane spring storage hole 80, a vane spring 8 arranged in series with the vane 7 is accommodated. The vane spring 8 is such that the tip of the vane 7 is pressed against the outer circumferential surface of the rolling piston 6. The vane spring 8 is composed of, for example, a coil spring.

Next, the operation of the rotary compressor 100 of the first embodiment will be described. In this rotary compressor (100), the refrigerant of the accumulator (12) is introduced into the compression chamber of the cylinder chamber (50) through the suction pipe (10) and the suction port, and then the electric motor (2) is driven. In the rotary compressor 100, when the electric motor part 2 is driven, the rolling piston 6 fitted to the eccentric shaft part 42 of the crankshaft 4 eccentrically rotates, and refrigerant is compressed in the cylinder chamber 50. do. The refrigerant compressed in the cylinder chamber 50 is discharged from the discharge hole of the upper shaft 51 into the space of the discharge muffler, and then discharged from the discharge hole of the discharge muffler into the sealed container 1. The discharged refrigerant is discharged from the discharge pipe (11).

By the way, the rotary compressor 100 forms a long vane groove 70, widens the sliding area between the vane 7 and the vane groove 70, and slides the vane 7 and the vane groove 70. Stabilizing is effective for improving reliability. On the other hand, in order to add the vane 7 with the vane spring 8 and follow the rolling piston 6, it is necessary to sufficiently secure the length of the vane spring storage hole 80. Therefore, in the rotary compressor 100, when the vane groove 70 becomes long, the hermetic container 1 also expands as much, and the entire apparatus becomes large.

Therefore, in the cylinder 5 in the first embodiment, as shown in FIGS. 2 and 3, the vane spring groove 9 for extending the vane spring storage hole 80 is around the vane groove 70. Thus, it is formed from the vane spring storage hole 80 toward the cylinder chamber 50. That is, the vane spring 8 is accommodated in the vane spring storage hole 80 and the vane spring groove 9, and reciprocates in the vane spring storage hole 80 and the vane spring groove 9. In addition, the length of the vane spring groove 9 is set to be appropriately changed depending on the structure of the compressor or the type of refrigerant.

As shown in Fig. 4, the vane spring groove 9 is formed in an annular shape corresponding to the shape of the vane spring 8, and is formed so that a part of the vane groove 70 vertically elongated intersects. This is because the vane spring receiving hole 80 is extended, and the front end of the vane 7 is pushed with the vane spring 8 so as to press firmly against the outer circumferential surface of the rolling piston 6. Since the vane spring groove 9 needs to pass through the vane spring 8, the outer diameter is larger than the outer diameter of the vane spring 8, and the inner diameter is smaller than the inner diameter of the vane spring 8.

In addition, the size and shape of the vane spring groove 9 are not limited to the illustrated form. The vane spring groove (9) can extend the vane spring receiving hole (80), and the received vane spring (8) can be forced to press the tip of the vane (7) firmly against the outer circumferential surface of the rolling piston (6). If so, another form may be used.

As described above, according to the rotary compressor 100 according to the first embodiment, even if the length of the vane spring storage hole 80 is shortened, the vane 7 is provided by the vane spring 8 stored in the vane spring groove 9. ) Can be added, so that the rolling piston 6 can follow. Therefore, since the rotary compressor 100 can form the vane groove 70 as long as the length of the vane spring storage hole 80 is shortened, the sliding area of the vane 7 and the vane groove 70 Can widen and improve the reliability.

In addition, the vane spring groove 9 is an annular shape corresponding to the coil-shaped vane spring 8. Therefore, since the rotary compressor 100 according to the first embodiment can smoothly receive the vane spring 8 in the vane spring groove 9, the vane 7 is added to the vane spring 8 to add a rolling piston. The function to follow (6) can be enhanced.

Here, the effect of the rotary compressor of the first embodiment will be described using specific numerical values. As an example, the dimensions of the rotary compressor 100 are assumed to be about 150 mm in outer diameter of cylinder 5 and about 70 mm in inner diameter. And, the outer diameter of the rolling piston 6 is about 45 mm, the length of the vane groove 70 is about 35 mm, the height of the vane 7 is about 20 mm, and the vane spring groove 9 is about 10 mm. The general heating operation conditions when operating the rotary compressor 100 are operating pressures, such that the suction pressure is about 0.2 MPaG and the discharge pressure is about 4.2 MPaG. The driving frequency is about 120 rpms.

In general, the trickiness of the sliding condition of the vane 7 and the vane groove 70 is represented by a PV value that is the product of the pressure P supporting the vane 7 and the operating speed V of the vane 7. The pressure P is the difference between the suction pressure and the discharge pressure divided by the sliding area of the vane 7 and the vane groove 70. When the PV value is more than 9.00 W/㎟, the sliding conditions of the vane 7 and the vane groove 70 are difficult, and a malfunction of the compressor due to a large difference between the suction pressure and the discharge pressure occurs, so that the vane groove 70 Therefore, surface treatment such as manganese treatment is required.

In the rotary compressor 100 of the first embodiment, the vane spring groove 9 is provided, and since the sliding area of the vane 7 and the vane groove 70 is increased, the PV value becomes 7.00 W/mm 2 , The surface treatment of the vane groove 70 becomes unnecessary. On the other hand, in the conventional rotary compressor, since the length of the vane groove can only be secured to 30 mm, the PV value becomes 9.00 W/mm 2, and the vane groove needs to be surface treated.

Next, the operating refrigerant of the rotary compressor 100 will be described. As the operating refrigerant of the rotary compressor 100, an HC refrigerant such as propane or R1234yf or an HFO refrigerant may be used in addition to the R410A refrigerant. Since the HC refrigerant and the HFO refrigerant have a small difference between the suction pressure and the discharge pressure, the pressure supporting the vane 7 becomes small, and a base spring force stronger than that of the R410A refrigerant is required. For example, the dimensions of the rotary compressor 100 are assumed to be about 160 mm in outer diameter of cylinder 5 and about 70 mm in inner diameter. And, the outer diameter of the rolling piston 6 is about 45 mm, the length of the vane groove 70 is about 40 mm, the height of the vane 7 is about 20 mm, and the vane spring groove 9 is about 20 mm. In the case where propane is used as the working refrigerant, the general heating operation conditions when operating the rotary compressor are the working pressure, the suction pressure being about 0.2 MPa, and the discharge pressure being about 2.0 MPa. The driving frequency is about 120 rpms.

The PV value based on the above value is 7.08 W/mm 2. Therefore, in the rotary compressor 100 of Embodiment 1, the surface treatment of the vane groove 70 is unnecessary. On the other hand, in the conventional rotary compressor, since the length of the vane groove can only be secured, for example, about 10 mm, the PV value becomes 14.17 W/mm 2, so that the vane groove needs surface treatment. As described above, in the rotary compressor 100 according to the first embodiment, reliability can be improved even when an HC refrigerant or an HFO refrigerant is used as the operation refrigerant.

Next, a modified example of the rotary compressor according to the first embodiment will be described with reference to Figs. 5 and 6. 5 is a modification of the rotary compressor according to the first embodiment of the present invention, and is a cross-sectional view showing the main part of the compressor mechanism. 6 is a cross-sectional view showing only the cylinder of the compression mechanism portion shown in FIG. 5.

In the rotary compressor shown in Figs. 5 and 6, the vane spring groove 9 extending the vane spring receiving hole 80 is directed toward the cylinder chamber 50 from a position near the outer circumferential surface of the cylinder 5 to the vane groove. It is formed around 70. The vane spring storage hole 80 is fooled to fix the end turn of the vane spring 8. That is, in the rotary compressor shown in FIGS. 5 and 6, the length of the vane spring storage hole 80 is made as short as possible, and the vane groove 70 is formed to be longer, so that the vane 7 and the vane groove ( The slide area of 70) can be secured wide.

Embodiment 2.

Next, the rotary compressor according to Embodiment 2 of the present invention will be described based on FIG. 7. 7 is a cross-sectional view showing a cylinder of a rotary compressor according to Embodiment 2 of the present invention. In addition, about the same structure as the rotary compressor demonstrated by Embodiment 1, the same code|symbol is attached|subjected, and the description is abbreviate|omitted suitably.

In the rotary compressor according to the second embodiment, the vane spring groove 9 has an inclined portion 81 connecting the side wall of the vane spring receiving hole 80 to the side wall of the vane groove 70, and the vane spring groove 9 is inclined portion 81. It is characterized in that it is formed toward the cylinder chamber 50 from. When the vane spring storage hole 80 is formed by drilling, the end portion on the cylinder chamber 50 side may have a triangular shape roughly the same as the shape of the tip of the drill. Even in such a case, the vane spring groove 9 can be formed from the inclined portion 81 toward the cylinder chamber 50, so that the vane spring storage hole 80 can be extended.

Here, the effect of the rotary compressor of the second embodiment will be described using specific numerical values. As an example, the rotary compressor has an outer diameter of about 140 mm and an inner diameter of about 70 mm as an example. The outer diameter of the rolling piston 6 is about 45 mm, the length of the vane groove 70 is about 30 mm, the height of the vane 7 is about 20 mm, the vane spring groove 9 is about 10 mm, the inclined portion 81 ) Is about 10 mm long. The general cooling operation conditions when operating the rotary compressor are the operating pressures, such that the suction pressure is about 1.0 MPaG and the discharge pressure is about 3.5 MPaG. The driving frequency is about 120 rpms.

The PV value based on the above value is 6.56 W/mm 2. Therefore, in the rotary compressor of Embodiment 2, the surface treatment of the vane groove 70 is unnecessary. On the other hand, in the conventional rotary compressor, since the length of the vane groove can only be secured, for example, about 20 mm, the PV value becomes 9.84 W/mm 2, and surface treatment of the vane groove is required.

Therefore, like the rotary compressor of the second embodiment, the vane spring receiving hole 80 has an inclined portion 81 connecting the side wall of the vane spring receiving hole 80 to the side wall of the vane groove 70, and the vane spring groove Even when (9) is formed from the inclined portion 81 toward the cylinder chamber 50, the same operational effects as the rotary compressor of the first embodiment can be obtained.

Embodiment 3.

Next, the rotary compressor according to Embodiment 3 of the present invention will be described based on FIGS. 8 and 9. 8 is a cross-sectional view showing a main part of a compressor mechanism portion of a rotary compressor according to Embodiment 3 of the present invention. 9 is a cross-sectional view showing only the cylinder of the compression mechanism portion shown in FIG. 8. In addition, about the same structure as the rotary compressor demonstrated by Embodiment 1, the same code|symbol is attached|subjected, and the description is abbreviate|omitted suitably.

In the rotary compressor according to the third embodiment, as shown in Figs. 8 and 9, a vane spring 8 for urging the tip of the vane 7 against the outer circumferential surface of the rolling piston 6 is a cylinder ( It is configured to be received in the vane spring groove 90 formed in 5). The vane spring groove 90 is formed around the vane groove 70 toward the cylinder chamber 50 from the outer circumferential surface of the cylinder 5.

The cross section seen from the arrow A-A shown in FIG. 9 is the same as the shape shown in FIG. 4 described in the first embodiment. That is, the vane spring groove 90 of the rotary compressor according to the third embodiment is also formed in an annular shape corresponding to the shape of the coil-shaped vane spring 8, and a part of the vane groove 70 vertically elongated crosses It is formed to. Therefore, since this vane spring 8 can smoothly store the vane spring 8 in the vane spring groove 90, the vane spring 8 is added with the vane 7 to follow the rolling piston 6. Can be increased.

In addition, since the vane spring groove 90 needs to pass through the vane spring 8, the outer diameter is larger than the outer diameter of the vane spring 8, and the inner diameter is smaller than the inner diameter of the vane spring 8. In addition, the size and shape of the vane spring groove 90 are not limited to the illustrated form. The vane spring groove 90 may be of another form as long as the vane spring 8 accommodated can be pressed so that the tip of the vane 7 is pressed against the outer circumferential surface of the rolling piston 6.

Therefore, the rotary compressor of Embodiment 3 can follow the rolling piston 6 by adding the vane 7 with the vane spring 8 accommodated in the vane spring groove 90 having a sufficient length. In addition, since the rotary compressor can form the vane groove 70 in the radial direction of the cylinder 5 regardless of the length of the vane spring groove 90, the vane 7 and the vane groove 70 are Since the sliding area can be enlarged, reliability can be improved.

Here, the effect of the rotary compressor of the third embodiment will be described using specific numerical values. The dimensions of the rotary compressor are, for example, the outer diameter of the cylinder 5 of about 160 mm and the inner diameter of about 70 mm. The outer diameter of the rolling piston 6 is about 45 mm, the length of the vane groove 70 is about 40 mm, the height of the vane 7 is about 20 mm, and the vane spring groove 90 is about 20 mm. The general heating operation conditions when the rotary compressor is operated are operating pressures, such that the suction pressure is about 0.2 MPaG and the discharge pressure is about 4.7 MPaG. The driving frequency is about 120 rpms.

The PV value based on the above value is 8.85 W/mm 2. Therefore, in the rotary compressor of the third embodiment, surface treatment of the vane groove 70 is unnecessary. On the other hand, in the conventional rotary compressor, since the length of the vane groove can only be secured, for example, about 20 mm, the PV value becomes 17.71 W/mm 2, and the surface treatment of the vane groove 70 is required.

Although the present invention has been described above based on the embodiments, the present invention is not limited to the configuration of the above-described embodiments. For example, the internal configuration of the illustrated rotary compressor 100 is an example, and is not limited to the above, and a rotary compressor including other components can be similarly implemented. Specifically, it is a twin rotary compressor including two compression chambers. In short, the present invention is intended to cover a range of design changes and application changes commonly performed by those skilled in the art without departing from the technical spirit.

1: Airtight container
2: Motor part
3: Compressor section
4: crankshaft
5: cylinder
6: rolling piston
7: Bain
8: vane spring
9: Bain Spring Home
10: suction tube
11: discharge pipe
12: accumulator
20: stator
21: rotor
40: main shaft
41: supporting part
42: eccentric shaft
50: cylinder room
51: upper shaft
52: lower shaft
70: vane home
80: vane spring storage hole
81: slope
90: vane spring groove
100: rotary compressor

Claims (4)

In the sealed container, an electric motor unit and a compressor mechanism for compressing refrigerant by a driving force transmitted from the electric motor unit are provided.
The compressor portion,
A crankshaft having an eccentric shaft portion and being rotationally driven by the electric motor portion,
A cylinder fixed to the sealed container and having a cylinder chamber,
A shaft bearing provided on both end surfaces of the cylinder and closing the cylinder chamber,
A rolling piston fitted to the eccentric shaft portion and accommodated in the cylinder chamber, and eccentrically rotates with the eccentric shaft portion to compress refrigerant;
A vane provided in a vane groove formed in the radial direction of the cylinder, and partitioning the cylinder chamber into a suction chamber and a compression chamber,
It is accommodated in the vane spring receiving hole formed in the cylinder, and has a vane spring for urging the tip of the vane to press against the outer circumferential surface of the rolling piston.
A rotary compressor, characterized in that, in the cylinder, a vane spring groove extending the vane spring receiving hole is formed around the vane groove from the vane spring receiving hole toward the cylinder chamber. According to claim 1,
The vane spring storage hole has an inclined portion connecting the side wall of the vane groove from the side wall of the vane spring storage hole,
The vane spring groove is a rotary compressor, characterized in that formed from the inclined portion toward the cylinder chamber. In the sealed container, an electric motor unit and a compressor mechanism for compressing refrigerant by a driving force transmitted from the electric motor unit are provided.
The compressor portion,
A crankshaft having an eccentric shaft portion and being rotationally driven by the electric motor portion,
A cylinder fixed to the sealed container and having a cylinder chamber,
A shaft bearing provided on both end surfaces of the cylinder and closing the cylinder chamber,
A rolling piston fitted to the eccentric shaft portion and accommodated in the cylinder chamber, and eccentrically rotates with the eccentric shaft portion to compress refrigerant;
A vane provided in a vane groove formed in the radial direction of the cylinder, and partitioning the cylinder chamber into a suction chamber and a compression chamber,
It is housed in a vane spring groove formed in the cylinder, and has a vane spring for urging the distal end of the vane to press against the outer circumferential surface of the rolling piston.
The vane spring groove, the rotary compressor, characterized in that the configuration formed from the outer peripheral surface of the cylinder toward the cylinder chamber around the vane groove. The method according to any one of claims 1 to 3,
The vane spring is coiled,
The vane spring groove is a rotary compressor, characterized in that the annular shape corresponding to the shape of the vane spring.

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