JP6869378B2 - Rotary compressor - Google Patents

Description

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

As disclosed in Patent Document 1, for example, the rotary compressor includes an electric motor unit and a compression mechanism unit driven by the electric motor unit in a closed 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. Further, the compression mechanism is housed in a rolling piston that is eccentrically rotated to compress the refrigerant and a vane spring storage 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 it.

Japanese Unexamined Patent Publication No. 11-022675

In general, in a rotary compressor, forming a long vane groove to widen the sliding area between the vane and the vane groove and stabilizing the sliding state of the vane and the vane groove is to improve reliability. It is valid. However, in order to urge the vane with the vane spring 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 lengthened, the closed container is also enlarged by that amount, and there is a problem that the entire device becomes large.

The present invention has been made to solve the above problems, and it is possible to increase the sliding area between the vane and the vane groove and improve the reliability without enlarging the closed container. , Aim to provide a rotary compressor.

The rotary compressor according to the present invention includes an electric motor unit and a compression mechanism unit that compresses a refrigerant by a driving force transmitted from the electric motor unit in a closed container, and the compression mechanism unit has an eccentric shaft portion. A crank shaft that is rotationally driven by the electric motor portion, a cylinder that is fixed to the closed container and has a cylinder chamber, bearings that are provided on both end faces of the cylinder and close the cylinder chamber, and an eccentric shaft. A rolling piston that is fitted into a portion and housed in the cylinder chamber and eccentrically rotates together with the eccentric shaft portion to compress the refrigerant, and a vane groove formed in the radial direction of the cylinder to suck the cylinder chamber. It has a vane that divides the chamber and a compression chamber, and a vane spring that is housed in a vane spring storage hole formed in the cylinder and urges the tip of the vane to press against the outer peripheral surface of the rolling piston. In the cylinder, a vane spring groove extending the vane spring storage hole is formed around the vane groove from the vane spring storage hole toward the cylinder chamber.

According to the rotary compressor according to the present invention, even if the length of the vane spring storage hole is shortened, the vane can be urged by the vane spring housed in the vane spring groove and can be made to follow the rolling piston. it can. Therefore, in the rotary compressor, the vane groove can be formed longer by the shorter the length of the vane spring storage hole, so that the sliding area between the vane and the vane groove can be widened and the reliability is improved. Can be made to.

It is a vertical cross-sectional view which roughly showed the whole structure of the rotary compressor which concerns on Embodiment 1 of this invention. It is sectional drawing which showed the main part of the compression mechanism part of the rotary compressor which concerns on Embodiment 1 of this invention. It is sectional drawing which showed the cylinder of the rotary compressor which concerns on Embodiment 1 of this invention. FIG. 3 is a cross-sectional view taken along the line AA shown in FIG. It is a modification of the rotary compressor which concerns on Embodiment 1 of this invention, and is the cross-sectional view which showed the main 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 sectional drawing which showed the cylinder of the rotary compressor which concerns on Embodiment 2 of this invention. It is sectional drawing which showed the main part of the compression mechanism part of the rotary compressor which concerns on 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 each figure, the same or corresponding parts are designated by the same reference numerals, and the description thereof will be omitted or simplified as appropriate. In addition, the shape, size, arrangement, etc. of the configurations shown in each figure can be appropriately changed within the scope of the present invention.

Embodiment 1.
First, the rotary compressor according to the first embodiment of the present invention will be described with reference to FIGS. 1 to 6. FIG. 1 is a vertical cross-sectional view schematically showing the overall structure of the rotary compressor according to the first embodiment of the present invention. FIG. 2 is a cross-sectional view showing a main part of the compression mechanism portion of the rotary compressor according to the first embodiment of the present invention. FIG. 3 is a cross-sectional view showing a cylinder of the rotary compressor according to the first embodiment of the present invention. FIG. 4 is a cross-sectional view taken along the line AA shown in FIG.

As shown in FIG. 1, the rotary compressor 100 according to the first embodiment has an electric motor unit 2 and a compression mechanism unit 3 that compresses a refrigerant by a driving force transmitted from the electric motor unit 2 inside the closed container 1. And, it is a configuration having. The electric motor unit 2 and the compression mechanism unit 3 are connected via a crankshaft 4. The refrigerant is, for example, R410 refrigerant.

The closed container 1 is connected to the accumulator 12 via a 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 so that the liquid refrigerant is not sucked into the compression mechanism 3 as much as possible. Further, a discharge pipe 11 for discharging the compressed refrigerant is connected to the upper part of the closed container 1. Refrigerating machine oil (not shown) is stored in the bottom of the closed container 1. The refrigerating machine oil mainly lubricates the sliding portion of the compression mechanism portion 3.

The electric motor unit 2 is composed of an annular stator 20 that is fixedly supported on the inner wall surface of the closed container 1 by shrink fitting or the like, and a rotor 21 that is rotatably provided so as to face the inner surface of the stator 20. It is configured. A crankshaft 4 is fitted in the rotor 21. The electric motor unit 2 is driven by being supplied with electric power from the outside via an airtight terminal (not shown).

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

The crankshaft 4 includes a spindle portion 40 fixed to the rotor 21 of the electric motor portion 2, a sub-spindle portion 41 provided on the opposite side of the spindle portion 40 with the cylinder 5 interposed therebetween, and a spindle portion 40 and a sub-shaft portion 41. It has an eccentric shaft portion 42 provided between the two. An oil suction hole is formed in 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 refrigerating machine oil stored in the bottom of the closed container 1 can be pumped up and supplied to the sliding portion of the compression mechanism portion 3. There is.

The outer peripheral portion of the cylinder 5 is fixed to the closed container 1 by a bolt or the like. As shown in FIG. 2, the cylinder 5 has a circular outer circumference, and a cylinder chamber 50, which is a circular space, is formed inside the cylinder 5. 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 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. Is blocked by. Further, 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 peripheral surface.

The upper bearing 51 is slidably fitted to the main shaft portion 40 of the crankshaft 4 and closes one end surface (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 sub-shaft 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 formed with a discharge hole for discharging the refrigerant compressed in the compression chamber. 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 rotates eccentrically together 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 that communicates with the cylinder chamber 50 and extends in the radial direction. The vane groove 70 is provided with a vane 7 slidably fitted to partition the cylinder chamber 50 into a suction chamber and a compression chamber. During the compression process, the vane 7 slides back and forth in the vane groove 70 following the eccentric rotation of the rolling piston 6 while the tip portion is in contact with the outer peripheral portion of the rolling piston 6. The cylinder chamber 50 is divided into a suction chamber and a compression chamber by abutting the tip of the vane 7 on the outer peripheral portion of the rolling piston 6. The vane 7 is made of, for example, a non-magnetic material.

Further, as shown in FIG. 2, the cylinder 5 is formed with a vane spring storage hole 80 on the back surface side of the vane groove 70. The inner diameter of the vane spring storage hole 80 is formed to be larger than the inner diameter of the vane groove 70. The vane spring 8 arranged in series with the vane 7 is housed in the vane spring storage hole 80. The vane spring 8 urges the tip of the vane 7 so as to press it against the outer peripheral 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 the 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 unit 2 is driven. In the rotary compressor 100, when the electric motor unit 2 is driven, the rolling piston 6 fitted to the eccentric shaft portion 42 of the crankshaft 4 rotates eccentrically, and the refrigerant is compressed in the cylinder chamber 50. The refrigerant compressed in the cylinder chamber 50 is discharged into the space of the discharge muffler from the discharge hole of the upper bearing 51, 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, it is reliable that the vane groove 70 is formed long, the sliding area between the vane 7 and the vane groove 70 is widened, and the sliding state of the vane 7 and the vane groove 70 is stabilized. It is effective in improving the sex. 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, in the cylinder 5 of the first embodiment, as shown in FIGS. 2 and 3, a vane spring groove 9 for extending the vane spring storage hole 80 is provided around the vane groove 70 from the vane spring storage hole 80. It is formed toward the chamber 50. That is, the vane spring 8 is housed 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. The length of the vane spring groove 9 shall be appropriately changed and formed according to the structure of the compressor or the type of the 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 as to partially intersect with the vertically long vane groove 70. This is because the vane spring 8 urges the tip of the vane 7 so as to press it 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 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.

The size and shape of the vane spring groove 9 are not limited to the illustrated form. The vane spring groove 9 has another form as long as the vane spring storage hole 80 can be extended and the stored vane spring 8 can be urged to press the tip of the vane 7 against the outer peripheral surface of the rolling piston 6. But it may be.

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 spring 8 housed in the vane spring groove 9 urges the vane 7. It can be made to follow the rolling piston 6. Therefore, in the rotary compressor 100, the vane groove 70 can be formed longer by the amount that the length of the vane spring storage hole 80 is shortened, so that the sliding area between the vane 7 and the vane groove 70 can be widened. , Reliability can be improved.

Further, the vane spring groove 9 is an annular shape corresponding to the coiled vane spring 8. Therefore, the rotary compressor 100 according to the first embodiment has a function of urging the vane 7 with the vane spring 8 to follow the rolling piston 6 because the vane spring 8 can be smoothly housed in the vane spring groove 9. 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 size of the rotary compressor 100 is such that 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. The general heating operation conditions for operating the rotary compressor 100 are an operating pressure of about 0.2 MPaG for the suction pressure and about 4.2 MPaG for the discharge pressure. The operating frequency is about 120 rps.

Generally, the severity of the sliding conditions of the vane 7 and the vane groove 70 is indicated by a PV value which 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 9.00 W / mm ² or more, the sliding conditions of the vane 7 and the vane groove 70 are strict, and the compressor fails due to the large difference between the suction pressure and the discharge pressure. Surface treatment such as manganese treatment is required for 70.

In the rotary compressor 100 of the first embodiment, the vane spring groove 9 is provided to increase the sliding area between the vane 7 and the vane groove 70, so that the PV value becomes 7.00 W / mm ² and the vane. 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 operating refrigerant of the rotary compressor 100 will be described. As the operating refrigerant of the rotary compressor 100, in addition to the R410A refrigerant, an HC refrigerant such as propane or R1234yf, or an HFO refrigerant may be used. Since the difference between the suction pressure and the discharge pressure of the HC refrigerant and the HFO refrigerant is small, the pressure supporting the vane 7 becomes small, and a stronger base spring force than the R410A refrigerant is required. For example, the dimensions of the rotary compressor 100 are 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, the general heating operating conditions for operating the rotary compressor are an suction pressure of about 0.2 MPaG and a discharge pressure of about 2.0 MPaG as the operating pressure. The operating frequency is about 120 rps.

The PV value based on the above numerical 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, the length of the vane groove can be secured only about 10 mm, for example, so that 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 the HC refrigerant or the HFO refrigerant is used as the operating refrigerant.

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

In the rotary compressor shown in FIGS. 5 and 6, a vane spring groove 9 for extending the vane spring storage hole 80 is formed around the vane groove 70 from a 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 end winding 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 storage hole 80 is made as short as possible, the vane groove 70 is formed longer, and the vane 7 and the vane groove 70 are slid. A wide moving area can be secured.

Embodiment 2.
Next, the rotary compressor according to the second embodiment of the present invention will be described with reference to FIG. 7. FIG. 7 is a cross-sectional view showing the cylinder of the rotary compressor according to the second embodiment of the present invention. The same configuration as that of the rotary compressor described in the first embodiment is designated by the same reference numerals, and the description thereof will be omitted as appropriate.

The rotary compressor according to the second embodiment has an inclined portion 81 connecting the side wall of the vane spring storage hole 80 to the side wall of the vane groove 70, and the vane spring groove 9 is directed 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 portion on the cylinder chamber 50 side may have 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 effect of the rotary compressor of the second embodiment will be described using specific numerical values. As an example, the dimensions of the rotary compressor are such that 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. The general cooling operation conditions for operating the rotary compressor are an operating pressure of about 1.0 MPaG for the suction pressure and about 3.5 MPaG for the discharge pressure. The operating frequency is about 120 rps.

The PV value based on the above numerical 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 only about, for example, about 20 mm, the PV value becomes 9.84 W / mm ² , and the surface treatment of the vane groove is required.

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

Embodiment 3.
Next, the rotary compressor according to the third embodiment of the present invention will be described with reference to FIGS. 8 and 9. FIG. 8 is a cross-sectional view showing a main part of the compression mechanism portion of the rotary compressor according to the third embodiment of the present invention. FIG. 9 is a cross-sectional view showing only the cylinder of the compression mechanism portion shown in FIG. The same configuration as that of the rotary compressor described in the first embodiment is designated by the same reference numerals, and the description thereof will be omitted as appropriate.

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 to be pressed against 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 the 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, and is formed so as to partially intersect with the vertically long vane groove 70. Has been done. Therefore, in this rotary compressor, the vane spring 8 can be smoothly housed in the vane spring groove 90, so that the function of urging the vane 7 with the vane spring 8 to follow the rolling piston 6 can be enhanced.

Since it is necessary to pass the vane spring 8 through the vane spring groove 90, 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. 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 stored vane spring 8 can be urged so as to press the tip end portion of the vane 7 against the outer peripheral surface of the rolling piston 6.

Therefore, in the rotary compressor of the third embodiment, the vane 7 can be urged by the vane spring 8 housed in the vane spring groove 90 having a sufficient length to follow the rolling piston 6. Further, in the rotary compressor, 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, so that the sliding area between the vane 7 and the vane groove 70 is widened. Can be done and reliability can be improved.

Here, the effect of the rotary compressor of the third embodiment will be described using specific numerical values. As an example, the dimensions of the rotary compressor are 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 90 is about 20 mm. The general heating operation conditions for operating the rotary compressor are an operating pressure of about 0.2 MPaG for the suction pressure and about 4.7 MPaG for the discharge pressure. The operating frequency is about 120 rps.

The PV value based on the above numerical 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 only about 20 mm, for example, 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 rotary compressor 100 shown in the figure is an example and is not limited to the above-mentioned contents, and the rotary compressor including other components can be similarly implemented. .. Specifically, it is a twin rotary compressor or the like equipped with two compression chambers. In short, the present invention includes a range of design changes and application variations normally performed by those skilled in the art, as long as the technical idea is not deviated.

1 Closed container, 2 Electric motor, 3 Compressor, 4 Crankshaft, 5 Cylinder, 6 Rolling piston, 7 Vane, 8 Bane spring, 9 Bane spring groove, 10 Suction pipe, 11 Discharge pipe, 12 Accumulator, 20 Fixed Child, 21 Rotor, 40 Main shaft, 41 Sub-shaft, 42 Eccentric shaft, 50 Cylinder chamber, 51 Upper bearing, 52 Lower bearing, 70 vane groove, 80 vane spring storage hole, 81 inclined part, 90 vane spring groove , 100 rotary compressor.

Claims (4)

An electric motor unit and a compression mechanism unit that compresses the refrigerant by a driving force transmitted from the electric motor unit are provided in a closed container.
The compression mechanism unit
A crankshaft having an eccentric shaft portion and being rotationally driven by the electric motor portion,
A cylinder fixed to the closed container and having a cylinder chamber,
Bearings provided on both end faces of the cylinder to close the cylinder chamber,
A rolling piston that is fitted into the eccentric shaft portion, housed in the cylinder chamber, and eccentricly rotates together with the eccentric shaft portion to compress the 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 has a vane spring that is housed in a vane spring storage hole formed in the cylinder and urges the tip of the vane to press against the outer peripheral surface of the rolling piston.
A rotary compressor in which a vane spring groove 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 storage hole has an inclined portion connecting the side wall of the vane spring storage hole to the side wall of the vane groove.
The rotary compressor according to claim 1, wherein the vane spring groove is formed from the inclined portion toward the cylinder chamber. An electric motor unit and a compression mechanism unit that compresses the refrigerant by a driving force transmitted from the electric motor unit are provided in a closed container.
The compression mechanism unit
A crankshaft having an eccentric shaft portion and being rotationally driven by the electric motor portion,
A cylinder fixed to the closed container and having a cylinder chamber,
Bearings provided on both end faces of the cylinder to close the cylinder chamber,
A rolling piston that is fitted into the eccentric shaft portion, housed in the cylinder chamber, and eccentricly rotates together with the eccentric shaft portion to compress the 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 has a vane spring that is housed in a vane spring groove formed in the cylinder and urges the tip of the vane to press against the outer peripheral surface of the rolling piston.
The rotary compressor has a structure in which the vane spring groove is formed around the vane groove from the outer peripheral surface of the cylinder toward the cylinder chamber. The vane spring is coiled and has a coil shape.
The rotary compressor according to any one of claims 1 to 3, wherein the vane spring groove is an annular shape corresponding to the shape of the vane spring.

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