WO2019142315A1

WO2019142315A1 - Rotary compressor

Info

Publication number: WO2019142315A1
Application number: PCT/JP2018/001563
Authority: WO
Inventors: 亮濱田
Original assignee: 三菱電機株式会社
Priority date: 2018-01-19
Filing date: 2018-01-19
Publication date: 2019-07-25
Also published as: JP6869378B2; CZ2020386A3; JPWO2019142315A1; CZ309161B6; KR20200087836A; CN111566351B; CN111566351A; KR102299099B1

Abstract

This rotary compressor comprises, within a hermetic container, an electric motor section, and a compression mechanism section in which a refrigerant is compressed by a drive force transmitted from the electric motor section. The compression mechanism section has: a crankshaft rotationally driven by the electric motor section; a cylinder having a cylinder chamber; a bearing which closes the cylinder chamber; a rolling piston which eccentrically rotates with an eccentric shaft section to compress the refrigerant; a vane which divides the cylinder chamber into a suction chamber and a compression chamber; and a vane spring which urges the front end of the vane so as to press the front end against the outer peripheral surface of the rolling piston. The cylinder has a vane spring groove which lengthens a vane spring containing hole, and the vane spring groove is formed around a vane groove so as to extend from the vane spring containing hole toward the cylinder chamber.

Description

Rotary compressor

The present invention relates to a rotary compressor used for a cooling device such as an air conditioner.

As disclosed in, for example, Patent Document 1, a rotary compressor includes a motor unit and a compression mechanism unit driven by the 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. The compression mechanism portion is housed in a cylinder chamber and is housed in a rolling piston that eccentrically rotates to compress a refrigerant, and is housed in a vane spring housing hole formed in the cylinder and presses the tip of the vane against the outer peripheral surface of the rolling piston It has a vane spring that urges in the same way.

Unexamined-Japanese-Patent No. 11-022675 gazette

Generally, in a rotary compressor, the vane groove is formed long to increase the sliding area between the vane and the vane groove, and the sliding condition between the vane and the vane groove is stabilized to improve the reliability. It is valid. However, in order for the vane spring to urge the vane to follow the rolling piston, it is necessary to secure a sufficient length of the vane spring storage hole. Therefore, in the rotary compressor, when the vane groove is made longer, the closed container is also expanded by that amount, and there is a problem that the entire apparatus becomes large.

The present invention has been made to solve the problems as described above, and the sliding area between the vane and the vane groove can be widened without increasing the closed container, and the reliability can be improved. , And a rotary compressor.

A rotary compressor according to the present invention includes a motor unit and a compression mechanism unit for compressing a refrigerant by a driving force transmitted from the motor unit in a sealed container, and the compression mechanism unit includes an eccentric shaft unit. A crank shaft rotatably driven by the motor unit, a cylinder fixed to the closed container and having a cylinder chamber, a bearing provided on both end surfaces of the cylinder and closing the cylinder chamber, the eccentric shaft A rolling piston which is fitted in a part and stored in the cylinder chamber, and is eccentrically rotated with the eccentric shaft to compress the refrigerant, and provided in a vane groove formed in a radial direction of the cylinder, and suctioning the cylinder chamber And a vane, which is divided into a chamber and a compression chamber, and a vane spring storage hole formed in the cylinder, and the tip end portion of the vane is the rolling piston A vane spring biased to press against the outer peripheral surface, and a vane spring groove for extending the vane spring storage hole is provided in the cylinder from the vane spring storage hole around the vane groove; It is formed towards the chamber.

According to the rotary compressor of the present invention, even if the length of the vane spring accommodation hole is shortened, the vane can be biased by the vane spring accommodated in the vane spring groove, and the rolling piston can be made to follow. it can. Therefore, in the rotary compressor, since the vane groove can be formed long by the length of the vane spring storage hole, the sliding area between the vane and the vane groove can be increased, and the reliability is improved. It can be done.

BRIEF DESCRIPTION OF THE DRAWINGS It is the longitudinal cross-sectional view which showed roughly the whole structure of the rotary compressor which concerns on Embodiment 1 of this invention. It is the cross-sectional view which showed the principal part of the compression mechanism part of the rotary compressor concerning Embodiment 1 of this invention. It is a cross-sectional view showing a cylinder of a rotary compressor concerning Embodiment 1 of the present invention. FIG. 4 is a cross-sectional view taken along line AA shown in FIG. 3; It is a modification of the rotary compressor concerning Embodiment 1 of this invention, Comprising: It is a cross-sectional view which showed the principal part of the compression mechanism part. It is a cross-sectional view which showed only the cylinder of the compression mechanism part shown in FIG. It is a cross-sectional view which showed the cylinder of the rotary compressor concerning Embodiment 2 of this invention. It is the cross-sectional view which showed the principal part of the compression mechanism part of the rotary compressor concerning Embodiment 3 of this invention. It is a cross-sectional view which showed only the cylinder of the compression mechanism part shown in FIG.

Hereinafter, embodiments of the present invention will be described with reference to the drawings. In the drawings, the same or corresponding parts will be denoted by the same reference numerals, and the description thereof will be appropriately omitted or simplified. Further, the configuration, size, arrangement and the like of the configuration described in each drawing can be appropriately changed within the scope of the present invention.

Embodiment 1
First, a rotary compressor according to a first embodiment of the present invention will be described based on FIGS. 1 to 6. FIG. 1 is a longitudinal sectional view schematically showing an entire structure of a rotary compressor according to a first embodiment of the present invention. FIG. 2 is a cross-sectional view showing the main parts of the compression mechanism of the rotary compressor according to Embodiment 1 of the present invention. FIG. 3 is a cross-sectional view showing a cylinder of the rotary compressor according to Embodiment 1 of the present invention. FIG. 4 is a sectional view taken along line AA shown in FIG.

As shown in FIG. 1, the rotary compressor 100 according to Embodiment 1 includes a motor unit 2 and a compression mechanism unit 3 that compresses a refrigerant by a driving force transmitted from the motor unit 2 inside the sealed container 1. And. The motor unit 2 and the compression mechanism unit 3 are connected via a crankshaft 4. The refrigerant is, for example, R410 refrigerant.

The sealed container 1 is connected to the accumulator 12 via the suction pipe 10, and the refrigerant gas is taken in from the accumulator 12. The accumulator 12 is provided to separate the refrigerant into a liquid refrigerant and a gas refrigerant and to prevent the liquid refrigerant from being sucked into the compression mechanism 3 as much as possible. Further, a discharge pipe 11 for discharging the compressed refrigerant is connected to an upper portion of the sealed container 1. At the bottom of the closed container 1, refrigeration oil (not shown) is stored. The refrigeration oil mainly lubricates the sliding portion of the compression mechanism 3.

The motor unit 2 includes an annular stator 20 fixedly supported on the inner wall surface of the sealed container 1 by shrink fitting or the like, and a rotor 21 rotatably provided opposite to the inner side surface of the stator 20. It is configured. The crankshaft 4 is inserted into the rotor 21. Electric power is supplied to the motor unit 2 from the outside through an airtight terminal (not shown) and driven.

As shown in FIGS. 1 and 2, the compression mechanism unit 3 includes a crankshaft 4 rotationally driven by the motor unit 2, a cylinder 5 having a cylinder chamber 50, and an upper bearing 51 as a bearing for closing the cylinder chamber 50. A lower bearing 52, a rolling piston 6, and a vane 7 are provided.

The crankshaft 4 has a main shaft portion 40 fixed to the rotor 21 of the motor portion 2, a sub shaft portion 41 provided on the opposite side of the main shaft portion 40 across the cylinder 5, a main shaft portion 40 and a sub shaft portion 41. And an eccentric shaft portion 42 provided therebetween. An oil suction hole is formed at the axial center of the crankshaft 4. The crankshaft 4 is provided with a spiral centrifugal pump in the oil suction hole so that the refrigeration oil stored in the bottom of the closed container 1 can be pumped up and supplied to the sliding portion of the compression mechanism 3 There is.

The cylinder 5 has an outer peripheral portion fixed to the closed container 1 by a bolt or the like. As shown in FIG. 2, the cylinder 5 has a circular outer periphery, and a cylinder chamber 50 which is a circular space is formed inside. The cylinder chamber 50 forms a compression chamber for compressing the refrigerant when driven. As shown in FIG. 1, both ends of the cylinder chamber 50 in the axial direction of the crankshaft 4 are open, and an upper bearing 51 provided on the upper surface of the cylinder 5 and a lower bearing 52 provided on the lower surface of the cylinder 5 are provided. Is blocked by Further, a suction port (not shown) through which refrigerant gas from the suction pipe 10 passes is provided in the cylinder 5 so as to penetrate the cylinder chamber 50 from the outer peripheral surface.

The upper bearing 51 is slidably fitted to the main shaft portion 40 of the crankshaft 4 and closes one end surface (the motor portion 2 side) of the cylinder chamber 50 of the cylinder 5. On the other hand, the lower bearing 52 is slidably fitted to the countershaft portion 41 of the crankshaft 4 and closes the other end surface (refrigerator oil side) of the cylinder chamber 50. Although not shown, the upper bearing 51 is provided with a discharge hole through which the refrigerant compressed in the compression chamber is discharged. Further, a discharge muffler is attached to the upper bearing 51 so as to cover the discharge hole.

The rolling piston 6 is formed in a ring shape, and is slidably fitted to 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.

As shown in FIG. 2, the cylinder 5 is formed with a vane groove 70 communicating with the cylinder chamber 50 and extending in the radial direction. In the vane groove 70, a vane 7 which divides the cylinder chamber 50 into a suction chamber and a compression chamber is slidably fitted. The vane 7 reciprocates within the vane groove 70 following the eccentric rotation of the rolling piston 6 while the tip end abuts against the outer peripheral portion of the rolling piston 6 during the compression process. The cylinder chamber 50 is divided into a suction chamber and a compression chamber when the tip end portion of the vane 7 abuts on the outer peripheral portion of the rolling piston 6. The vanes 7 are made of, for example, a nonmagnetic material.

Further, as shown in FIG. 2, a vane spring housing hole 80 is formed on the back side of the vane groove 70 in the cylinder 5. The inner diameter of the vane spring housing hole 80 is formed larger than the inner diameter of the vane groove 70. The vane spring 8 disposed in series with the vane 7 is accommodated in the vane spring accommodation hole 80. The vane spring 8 biases the tip end of the vane 7 against the outer peripheral surface of the rolling piston 6. The vane spring 8 is formed of, for example, a coil spring.

Next, the operation of the rotary compressor 100 according to the first embodiment will be described. In the rotary compressor 100, after 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, the motor unit 2 is driven. In the rotary compressor 100, when the motor unit 2 is driven, the rolling piston 6 fitted to the eccentric shaft portion 42 of the crankshaft 4 is eccentrically rotated, and the refrigerant is compressed in the cylinder chamber 50. The refrigerant compressed in the cylinder chamber 50 is discharged from the discharge hole of the upper bearing 51 into the space of the discharge muffler, and then discharged into the closed container 1 from the discharge hole of the discharge muffler. The discharged refrigerant is discharged from the discharge pipe 11.

By the way, in the rotary compressor 100, the vane groove 70 is formed long to widen the sliding area between the vane 7 and the vane groove 70, and the sliding state between the vane 7 and the vane groove 70 is stabilized. It is effective in improving the quality. On the other hand, in order to urge the vane 7 with the vane spring 8 to follow the rolling piston 6, it is necessary to secure a sufficient length of the vane spring storage hole 80. Therefore, in the rotary compressor 100, when the vane groove 70 becomes long, the closed container 1 is also enlarged by that amount, and the entire apparatus becomes large.

Therefore, as shown in FIGS. 2 and 3, in the cylinder 5 in the first embodiment, the vane spring groove 9 for extending the vane spring accommodation hole 80 is formed from the vane spring accommodation hole 80 around the vane groove 70. It is formed toward the chamber 50. That is, the vane spring 8 is accommodated in the vane spring accommodation hole 80 and the vane spring groove 9, and reciprocates in the vane spring accommodation hole 80 and the vane spring groove 9. In addition, the length of the vane spring groove 9 shall be suitably changed and formed according to the structure of a compressor, or the kind of refrigerant | coolant.

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 as to partially cross the vertically elongated vane groove 70. This is because the vane spring 8 biases the tip end of the vane 7 against the outer peripheral surface of the rolling piston 6 while extending the vane spring storage hole 80. Since the vane spring groove 9 needs to pass 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.

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 storage hole 80, and if the stored vane spring 8 can urge the tip end portion of the vane 7 to press the outer peripheral surface of the rolling piston 6, another embodiment May be.

As described above, according to the rotary compressor 100 according to the first embodiment, the vane spring 8 is biased by the vane spring 8 stored in the vane spring groove 9 even if the length of the vane spring storage hole 80 is shortened. And the rolling piston 6 can be made to follow. Therefore, the rotary compressor 100 can form the vane groove 70 longer by an amount corresponding to the shortening of the length of the vane spring accommodation hole 80, so the sliding area between the vane 7 and the vane groove 70 can be increased. , Can improve the reliability.

Further, the vane spring groove 9 has an annular shape corresponding to the coiled vane spring 8. Therefore, the rotary compressor 100 according to the first embodiment can smoothly store the vane spring 8 in the vane spring groove 9, so that the vane spring 8 urges the vane 7 to follow the rolling piston 6. Can be enhanced.

Here, the effects of the rotary compressor according to the first embodiment will be described using specific numerical values. As an example of the dimensions of the rotary compressor 100, the outer diameter of the cylinder 5 is about 150 mm and the inner diameter is about 70 mm. 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. As a general heating operation condition at the time of operating the rotary compressor 100, the suction pressure is about 0.2 MPaG and the discharge pressure is about 4.2 MPaG as an operating pressure. The operating frequency is about 120 rps.

In general, the severity of the sliding conditions of the vanes 7 and the vane grooves 70 is indicated by a PV value which is the product of the pressure P supporting the vanes 7 and the operating speed V of the vanes 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 9.00 W / mm ² or more, the sliding condition of the vane 7 and the vane groove 70 is severe, and the compressor failure occurs due to the large difference between the suction pressure and the discharge pressure. 70 requires surface treatment such as manganese treatment.

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

Next, the operation refrigerant of the rotary compressor 100 will be described. The operating refrigerant of the rotary compressor 100 may use an HC refrigerant such as propane or R1234yf or an HFO refrigerant 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 for supporting the vanes 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 set such that the outer diameter of the cylinder 5 is about 160 mm and the inner diameter is 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 9 is about 20 mm. When propane is used as the operating refrigerant, general heating operating conditions for operating the rotary compressor are, as operating pressure, a suction pressure of about 0.2 MPaG and a discharge pressure of about 2.0 MPaG. The operating frequency is about 120 rps.

The PV value based on the above value is 7.08 W / mm ² . Therefore, in the rotary compressor 100 of the first embodiment, 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 be secured, for example, only about 10 mm, the PV value is 14.17 W / mm ² and the vane groove needs to be surface-treated. As described above, in the rotary compressor 100 according to the first embodiment, the reliability can be improved even when using the HC refrigerant or the HFO refrigerant as the operating refrigerant.

Next, a modification of the rotary compressor according to the first embodiment will be described based on FIGS. 5 and 6. FIG. 5 is a modified example of the rotary compressor according to Embodiment 1 of the present invention, and is a cross-sectional view showing the main part of the compression mechanism. 6 is a cross-sectional view showing only the cylinder of the compression mechanism shown in FIG.

In the rotary compressor shown in FIGS. 5 and 6, the vane spring groove 9 for extending the vane spring accommodation hole 80 is formed around the vane groove 70 from the position near the outer peripheral surface of the cylinder 5 toward the cylinder chamber 50. ing. The vane spring storage hole 80 is provided to fix the wound portion of the vane spring 8. That is, the rotary compressor shown in FIGS. 5 and 6 has a configuration in which the length of the vane spring housing hole 80 is made as short as possible, and the vane groove 70 is formed longer to slide the vane 7 and the vane groove 70. A wide dynamic area can be secured.

Second Embodiment
Next, a rotary compressor according to a second embodiment of the present invention will be described based on FIG. FIG. 7 is a cross-sectional view showing a cylinder of a rotary compressor according to Embodiment 2 of the present invention. The same components as those of the rotary compressor described in the first embodiment are denoted by the same reference numerals, and the description thereof will be appropriately omitted.

The rotary compressor according to the second embodiment has the inclined portion 81 connecting the side wall of the vane groove 70 from the side wall of the vane spring accommodation hole 80, and the vane spring groove 9 extends from the inclined portion 81 toward the cylinder chamber 50. It is characterized by being formed. When the vane spring storage hole 80 is formed by drilling, the end on the cylinder chamber 50 side may be in a triangular shape substantially the same as the tip shape 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, and the vane spring storage hole 80 can be extended.

Here, the effects of the rotary compressor according to the second embodiment will be described using specific numerical values. As for the dimensions of the rotary compressor, for example, the outer diameter of the cylinder 5 is about 140 mm and the inner diameter is about 70 mm. 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, and the length of the inclined portion 81 is about 10 mm. As a general cooling operation condition at the time of operating the rotary compressor, as the operating pressure, the suction pressure is about 1.0 MPaG and the discharge pressure is about 3.5 MPaG. The operating frequency is about 120 rps.

The PV value based on the above value is 6.56 W / mm ² . Therefore, in the rotary compressor of the second embodiment, 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 be secured, for example, only about 20 mm, the PV value is 9.84 W / mm ² and the surface treatment of the vane groove is required.

Therefore, as in the rotary compressor of the second embodiment, the vane spring accommodation hole 80 has the inclined portion 81 connecting the side wall of the vane groove 70 from the side wall of the vane spring accommodation hole 80, and the vane spring groove 9 is inclined. Even in the case of being formed from the portion 81 toward the cylinder chamber 50, the same function and effect as those of the rotary compressor of the first embodiment can be obtained.

Third Embodiment
Next, a rotary compressor according to a third embodiment of the present invention will be described based on FIG. 8 and FIG. FIG. 8 is a cross-sectional view showing the main parts of the compression mechanism of the rotary compressor according to Embodiment 3 of the present invention. FIG. 9 is a cross-sectional view showing only the cylinder of the compression mechanism shown in FIG. The same components as those of the rotary compressor described in the first embodiment are denoted by the same reference numerals, and the description thereof will be appropriately omitted.

In the rotary compressor according to the third embodiment, as shown in FIG. 8 and FIG. 9, the vane spring 8 urging the tip end of the vane 7 to press the outer peripheral surface of the rolling piston 6 is formed in the cylinder 5 It is configured to be housed in the vane spring groove 90. The vane spring groove 90 is formed around the vane groove 70 from the outer peripheral surface of the cylinder 5 toward the cylinder chamber 50.

The cross section taken along line AA 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 coiled vane spring 8 so that it partially intersects the vertically elongated vane groove 70. It is done. Therefore, since this rotary compressor can smoothly accommodate the vane spring 8 in the vane spring groove 90, the function of urging the vane 7 by the vane spring 8 to follow the rolling piston 6 can be enhanced.

Since the vane spring groove 90 needs to pass the vane spring 8, the outside diameter is larger than the outside diameter of the vane spring 8 and the inside diameter is smaller than the inside diameter of the vane spring 8. Further, the size and shape of the vane spring groove 90 are not limited to the illustrated form. The vane spring groove 90 may have another form as long as the housed vane spring 8 can urge the tip end portion of the vane 7 against the outer peripheral surface of the rolling piston 6.

Therefore, in the rotary compressor according to the third embodiment, the vane 7 can be urged by the vane spring 8 accommodated in the vane spring groove 90 having a sufficient length to follow the rolling piston 6. Further, in the rotary compressor, since the vane groove 70 can be formed long in the radial direction of the cylinder 5 regardless of the length of the vane spring groove 90, the sliding area between the vane 7 and the vane groove 70 is increased. The reliability can be improved.

Here, the effects of the rotary compressor according to the third embodiment will be described using specific numerical values. As for the dimensions of the rotary compressor, for example, the outer diameter of the cylinder 5 is about 160 mm and the inner diameter is 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. As a general heating operation condition at the time of operating the rotary compressor, as an operating pressure, a suction pressure is about 0.2 MPaG and a discharge pressure is about 4.7 MPaG. The operating frequency is about 120 rps.

The PV value based on the above value is 8.85 W / mm ² . Therefore, in the rotary compressor of the third embodiment, 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 be secured, for example, only about 20 mm, the PV value is 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 embodiment, the present invention is not limited to the configuration of the embodiment described above. For example, the internal configuration of the illustrated rotary compressor 100 is merely an example, and the present invention is not limited to the above-described content, and the present invention can be similarly implemented even in a rotary compressor including other components. . Specifically, it is a twin rotary compressor or the like provided with two compression chambers. In short, the present invention includes the scope of variations in design changes and applications which are ordinarily made by those skilled in the art without departing from the technical concept of the present invention.

Reference Signs List 1 sealed container, 2 motor unit, 3 compression mechanism unit, 4 crankshaft, 5 cylinder, 6 rolling piston, 7 vane, 8 vane spring, 9 vane spring groove, 10 suction pipe, 11 discharge pipe, 12 accumulator, 20 fixed 21 rotor, 40 main shaft portion, 41 sub shaft portion, 42 eccentric shaft portion, 50 cylinder chamber, 51 upper bearing, 52 lower bearing, 70 vane groove, 80 vane spring storage hole, 81 inclined portion, 90 vane spring groove , 100 rotary compressors.

Claims

The sealed container includes a motor unit and a compression mechanism unit that compresses a refrigerant by a driving force transmitted from the motor unit.
The compression mechanism unit is
A crankshaft which has an eccentric shaft portion and is rotationally driven by the motor portion;
A cylinder fixed to the closed container and having a cylinder chamber;
Bearings provided on both end surfaces of the cylinder and closing the cylinder chamber;
A rolling piston which is fitted to the eccentric shaft portion and accommodated in the cylinder chamber and is eccentrically rotated with the eccentric shaft portion to compress the refrigerant;
A vane which is provided in a vane groove formed in a radial direction of the cylinder and which divides the cylinder chamber into a suction chamber and a compression chamber;
And a vane spring housed in a vane spring housing hole formed in the cylinder and biasing the tip end of the vane against the outer peripheral surface of the rolling piston.
The rotary compressor, wherein a vane spring groove for extending the vane spring storage hole is formed in the cylinder around the vane groove from the vane spring storage hole toward the cylinder chamber.
The vane spring receiving hole has an inclined portion connecting the side wall of the vane groove from the side wall of the vane spring receiving hole,
The rotary compressor according to claim 1, wherein the vane spring groove is formed from the inclined portion toward the cylinder chamber.
The sealed container includes a motor unit and a compression mechanism unit that compresses a refrigerant by a driving force transmitted from the motor unit.
The compression mechanism unit is
A crankshaft which has an eccentric shaft portion and is rotationally driven by the motor portion;
A cylinder fixed to the closed container and having a cylinder chamber;
Bearings provided on both end surfaces of the cylinder and closing the cylinder chamber;
A rolling piston which is fitted to the eccentric shaft portion and accommodated in the cylinder chamber and is eccentrically rotated with the eccentric shaft portion to compress the refrigerant;
A vane which is provided in a vane groove formed in a radial direction of the cylinder and which divides the cylinder chamber into a suction chamber and a compression chamber;
And a vane spring housed in a vane spring groove formed in the cylinder and biasing the tip end of the vane against the outer peripheral surface of the rolling piston.
The rotary compressor, wherein the vane spring groove is formed around the vane groove from an outer peripheral surface of the cylinder toward the cylinder chamber.
The vane spring is coiled,
The rotary compressor according to any one of claims 1 to 3, wherein the vane spring groove has an annular shape corresponding to the shape of the vane spring.