JP7595403B2 - Rotary Compressor - Google Patents

Description

The present invention relates to a rotary compressor.

2. Description of the Related Art One type of compressor used in refrigeration systems, air conditioners, and the like is a rotary compressor (see, for example, Patent Document 1).
Such a rotary compressor includes a cylinder, a shaft, an upper bearing, a lower bearing, a piston rotor, blades (vanes), and a housing that accommodates these.

The cylinder has a cylindrical compression chamber and a blade accommodating groove extending in a radial direction. The shaft has a shaft body that passes through the compression chamber and an eccentric shaft portion that is provided on the shaft body and disposed in the compression chamber.
The upper bearing is disposed at an upper end of the cylinder so as to close an upper end of the compression chamber. The lower bearing is disposed at a lower end of the cylinder so as to close a lower end of the compression chamber. The upper bearing and the lower bearing support the shaft body in a rotatable manner.

The piston rotor is provided on the outer periphery of the eccentric shaft portion. A part of the outer periphery of the piston rotor is in contact with the inner periphery of the compression chamber. The piston rotor rolls along the inner periphery of the compression chamber.
The blades are disposed in the blade receiving grooves and move in the radial direction while being in contact with the outer circumferential surface of the piston rotor The blades separate the compression chamber into a low pressure chamber and a high pressure chamber.

JP 2018-115566 A

In recent years, in order to reduce the outer diameter of rotary compressors (outer diameter of the housing), there has been a demand to reduce the outer diameter of the cylinder while preventing a decrease in the strength of the blades, thereby reducing the outer diameter of the rotary compressor.

The present invention aims to provide a rotary compressor that can reduce the outer diameter of the rotary compressor while preventing a decrease in blade strength.

In order to solve the above problems, a rotary compressor according to one aspect of the present invention includes: a cylinder body accommodated in a housing, a cylindrical compression chamber formed in the cylinder body, and a blade accommodating groove formed in the cylinder body, the cylinder body communicating with the compression chamber and extending from an inner circumferential surface of the compression chamber radially outward of the cylinder body, an upper bearing arranged on an upper surface of the cylinder so as to close an upper end of the compression chamber, a lower bearing arranged on a lower surface of the cylinder so as to close a lower end of the compression chamber, a shaft body rotatably supported by the upper and lower bearings and inserted into the compression chamber, and a shaft arranged on the shaft body and having an eccentric shaft portion arranged in the compression chamber, a piston rotor arranged outside the eccentric shaft portion and rolling along the inner circumferential surface of the compression chamber, and a blade at least partially arranged in the blade accommodating groove, the blade moving in the radial direction of the cylinder body with a tip arranged on the compression chamber side being in contact with an outer circumferential surface of the piston rotor, the blade separating the compression chamber into a low pressure chamber and a high pressure chamber, a blade pressing member that is provided in the blade accommodating groove and presses a tip of the blade against an outer peripheral surface of the piston rotor, wherein, when an inner diameter of the compression chamber is Dc, a length of the blade in a radial direction of the cylinder body is L, and a thickness of the blade in a circumferential direction of the cylinder body is t, the following formulas (1), (2) , (3), and (4) are satisfied:
L/Dc≦0.4 (1)
0.2≦t/L...(2)
0.2≦L/Dc...(3)
t/L≦0.5...(4)
The blade has a blade body and a hard coating covering a surface of the blade body,
The maximum value of the blade protruding amount, which is the amount by which the blade protrudes into the compression chamber, is 50% or more and 70% or less of the length L of the blade .

According to the present invention, by setting the blade length L and blade thickness t so as to satisfy the above formulas (1) and (2), it is possible to shorten the blade length L while setting the thickness t so as to maintain the strength of the blade.

For example, if the length of a blade is shortened without changing the thickness of the blade, the area of the side surface of the blade arranged in the circumferential direction of the cylinder becomes smaller, and the force per unit area that the side surface of the blade receives increases.
On the other hand, as described above, by shortening the length L of the blade and setting the thickness t at which the strength of the blade can be maintained, it is possible to suppress a decrease in the strength of the blade.
Furthermore, by shortening the length L of the blades, it is possible to reduce the outside diameter of the cylinder, and therefore the outside diameter of the rotary compressor (the outside diameter of the housing) can be reduced.

In addition, by shortening the length L of the blade, the distance from the position (fulcrum) of the blade where the blade intersects with the inner circumferential surface of the compression chamber to the rear end of the blade housed in the blade housing groove is shortened. This makes it possible to reduce the moment that the rear end of the blade receives due to the force that the tip of the blade receives from the rolling piston rotor.

In this way, by setting the inner diameter Dc of the compression chamber and the length L of the blade so as to satisfy the above formula (3), it is possible to prevent the blade from falling out of the blade storage groove.

In this way, by setting the blade length L and blade thickness t to satisfy the above formula (4), it is possible to prevent the blade thickness t from becoming too thin compared to the blade length L. This makes it possible to prevent a decrease in the strength of the blade.

In this way, the blade has a hard coating that covers the surface of the blade body, which makes it possible to reinforce the strength of the blade body. This improves the strength of the blade.

For example, if the maximum amount of protrusion of the blade (hereinafter referred to as the "maximum amount of protrusion of the blade") is less than 50% of the length of the blade, the effect of reducing the outer diameter of the cylinder is reduced.
On the other hand, if the maximum protrusion amount of the blade is greater than 70% of the blade length, the length of the blade accommodated in the blade accommodating groove becomes too short, causing the tip side of the blade to oscillate significantly in the circumferential direction of the piston rotor.
This may result in poor contact of the tips of the blades with the outer circumferential surface of the piston rotor, which may make it difficult to separate the low pressure chamber 52A from the high pressure chamber 52B using the blades.
Therefore, by making the blade length L 50% or more and 70% or less, it is possible to separate the low pressure chamber and the high pressure chamber using the blade and reduce the outer diameter of the cylinder.

According to the present invention, it is possible to reduce the outer diameter of the rotary compressor while suppressing the deterioration of the blade strength.

1 is a cross-sectional view showing a schematic configuration of a rotary compressor according to an embodiment of the present invention. 2 is a cross-sectional view taken along line A ₁ -A ₂ of the rotary compressor shown in FIG. 1 . 3 is a cross-sectional view of the blade cut by a virtual plane perpendicular to the longitudinal direction of the blade shown in FIG. 2, the cross-section being viewed from direction B. FIG.

(Embodiment)
A rotary compressor 10 according to the present embodiment will be described with reference to Figures 1 to 3. In Figure 1, _O1 indicates the axis of the shaft 24 (hereinafter referred to as "axis _O1 "), _O2 indicates the axis of the eccentric shaft portion 39 (hereinafter referred to as "axis _O2 "), and Z indicates the height direction (vertical direction) of the rotary compressor 10.
In FIG. 1, _R1 indicates the outer diameter of the housing 17 (cylindrical portion 33) (hereinafter referred to as "outer diameter _R1 "), and _R2 indicates the outer diameter of the cylinder 38 (hereinafter referred to as "outer diameter _R2 ").

In Figure 2, Dc indicates the inner diameter of the cylindrical compression chamber 52 (hereinafter referred to as "inner diameter Dc"), L indicates the length of the blade 45 (hereinafter referred to as "length L"), Ls indicates the length of the blade accommodating groove 53 (hereinafter referred to as "length Ls"), and Pmax indicates the maximum value of the blade protrusion amount, which is the amount by which the blade 45 protrudes into the compression chamber 52 (hereinafter referred to as "maximum protrusion amount Pmax").
In addition, in Figure 2, t indicates the thickness of the blade in the circumferential direction of the cylinder body 51 (hereinafter referred to as "thickness t"), P1 indicates the external force that the tip 45A of the blade 45 receives from the rolling piston rotor 41 (hereinafter referred to as "external force P1"), and P2 indicates the reaction force that the side surface 45a of the blade 45 receives from the external force (reaction force P2).
1 to 3, the same components are denoted by the same reference numerals.

The rotary compressor 10 has a compressor body 11, an accumulator 12, a bracket 13, and a suction pipe 14.
The compressor body 11 has a housing 17 , a guide pipe 18 , a compression section 21 , a shaft 24 , an upper bearing 26 , a lower bearing 27 , a motor section 29 , and a discharge pipe 31 .

The housing 17 is a sealed housing that defines a columnar internal space A. The housing 17 has a cylindrical portion 33, a bottom portion 34, and a lid portion 35.

The cylindrical portion 33 extends in the Z direction, and has an open upper and lower end. An intake hole 33A is formed in the lower portion of the cylindrical portion 33.

The bottom 34 is fixed to the cylindrical portion 33 with its upper portion inserted into the lower end of the cylindrical portion 33. In this way, the bottom 34 closes the lower end of the cylindrical portion 33. The lower portion of the bottom 34 protrudes downward from the lower end of the cylindrical portion 33.

The lid portion 35 is fixed to the cylindrical portion 33 with its lower portion inserted into the upper end of the cylindrical portion 33. The lid portion 35 has its upper portion protruding from the upper end of the cylindrical portion 33.
The lid portion 35 has a through portion 35A formed therein.

The guide pipe 18 is a cylindrical member with both ends open, and is fixed to the cylindrical portion 33 while inserted into the suction hole 33A. The suction tube 14 is inserted into the guide pipe 18. The guide pipe 18 guides the direction in which the suction tube 14 extends.

The compression portion 21 is accommodated within the housing 17 and is disposed at the lower part of the internal space A.
The compression section 21 has a cylinder 38 , an eccentric shaft portion 39 that constitutes the shaft 24 , a piston rotor 41 , a blade 45 , and a blade pressing member 47 .

The cylinder 38 has a cylinder body 51, a compression chamber 52, a blade accommodating groove 53, a refrigerant supply passage 55, and a discharge hole (not shown).
A portion of the outer circumferential surface of the cylinder body 51 is fixed to the inner circumferential surface 33 a of the lower part of the cylindrical portion 33 .
The compression chamber 52 is formed so as to penetrate through the center of the cylinder body 51. The compression chamber 52 is cylindrical and has an inner circumferential surface 52a.

The blade accommodating groove 53 is formed in the cylinder body 51. The blade accommodating groove 53 is in communication with the compression chamber 52 and extends from the inner peripheral surface 52a of the compression chamber 52 radially outward of the cylinder body 51. Of the ends of the blade accommodating groove 53, the end located on the outer peripheral side of the cylinder body 51 is located within the cylinder body 51. In other words, the blade accommodating groove 53 does not penetrate the cylinder body 51 radially.

The refrigerant supply passage 55 is formed in the cylinder body 51. The refrigerant supply passage 55 penetrates the cylinder body 51 arranged outside the compression chamber 52 in the radial direction.
As a result, one end of the refrigerant supply passage 55 located on the compression chamber 52 side communicates with the compression chamber 52 .
The other end of the refrigerant supply passage 55 is disposed to face the suction hole 33A formed in the cylindrical portion 33. The other end of the refrigerant supply passage 55 has a shape that allows the tip portion 14A of the suction pipe 14 to be attached thereto.
The refrigerant supply passage 55 configured as described above guides the gas-phase refrigerant supplied from the suction pipe 14 to the compression chamber 52 .

A discharge hole (not shown) is provided at a predetermined position in the cylinder body 51. The discharge hole communicates with the compression chamber 52 in a state in which the compressed gas-phase refrigerant (hereinafter referred to as "compressed refrigerant") can be discharged to the outside of the compression section 21. A reed valve (not shown) is provided in the discharge hole.

The eccentric shaft portion 39 is provided in a portion of a shaft main body 56 that constitutes the shaft 24 and extends in the Z direction, the portion being inserted into the compression chamber 52. As a result, the eccentric shaft portion 39 is disposed in the compression chamber 52. The eccentric shaft portion 39 has a cylindrical shape.
The axis _O2 of the eccentric shaft portion 39 is disposed at a position offset from the axis _O1 of the shaft body 56.

The piston rotor 41 has a housing portion 41A that houses the eccentric shaft portion 39. As a result, the piston rotor 41 is positioned outside the eccentric shaft portion 39 and is also positioned in the compression chamber 52. When the eccentric shaft portion 39 rotates, the piston rotor 41 rolls along the inner circumferential surface 52a of the compression chamber 52.

The blade 45 is a plate-shaped member, and at least a portion of the blade 45 is disposed within the blade accommodating groove 53. The blade 45 extends in the same direction as the blade accommodating groove 53 extends.
The blade 45 has a leading end 45A, a trailing end 45B, and side surfaces 45a and 45b.
The leading end 45A is a portion that comes into contact with the outer circumferential surface 41a of the rolling piston rotor 41. The rear end 45B is an end disposed on the opposite side to the leading end 45A, and is housed in the blade housing groove 53.

The side surfaces 45a and 45b are arranged in the circumferential direction of the cylinder body 51. The side surface 45a is the surface of the compression chamber 52 that is arranged on the low pressure chamber 52A side. When the tip 45A of the blade 45 receives an external force P1, the side surface 45a receives a reaction force P2. The side surface 45b is the surface that is arranged opposite the side surface 45a.

The blade 45 moves in the radial direction of the cylinder body 51 while being in contact with the outer circumferential surface 41 a of the piston rotor 41. In other words, as the piston rotor 41 rolls, the length of the blade 45 accommodated in the blade accommodation groove 53 (in other words, the amount of protrusion of the blade 45 protruding into the compression chamber 52) changes.
The blades 45 separate the compression chamber 52 into a low pressure chamber 52A having a low pressure and a high pressure chamber 52B having a higher pressure than the low pressure chamber.

The blade 45 may be composed of, for example, a blade body 45C and a hard coating 45D covering a surface 45Ca of the blade body 45C.
As the hard coating 45D, for example, a DLC (Diamond-Like-Carbon) coating, a chromium nitride film formed by a PVD method, or a tungsten carbide film can be used.

In this way, the blade 45 has a hard coating 45D that covers the surface 45Ca of the blade body 45C, which makes it possible to reinforce the strength of the blade body 45C. This improves the strength of the blade 45.

The length L of the blade 45 and the thickness t of the blade 45 are preferably set so as to satisfy the following formulas (5) and (6), where the inner diameter of the compression chamber 52 is Dc.
L/Dc≦0.4 (5)
0.2≦t/L...(6)

In this way, by setting the length L of the blade 45 and the thickness t of the blade 45 so as to satisfy the above formulas (5) and (6), it is possible to shorten the length L of the blade 45 while setting the thickness t such that the strength of the blade 45 can be maintained.

For example, if the length of the blade 45 is shortened without changing the thickness of the blade 45, the area of the side surface of the blade 45 arranged in the circumferential direction of the cylinder 38 becomes smaller, and the force per unit area received by the side surface of the blade becomes larger.
On the other hand, as described above, by shortening the length L of the blade 45 and setting the thickness t to a value that allows the strength of the blade 45 to be maintained, it is possible to prevent a decrease in the strength of the blade 45.
Furthermore, by shortening the length L of the blade 45, it is possible to reduce the outer diameter _R2 of the cylinder 38, so that the outer diameter of the rotary compressor 10 (the outer diameter of the housing 17 (the cylindrical portion 33)) can be reduced.

In addition, by shortening the length L of the blade 45, the distance from the position (fulcrum) of the blade 45 where the blade 45 intersects with the inner circumferential surface 52a of the compression chamber 52 to the rear end 45B of the blade 45 housed in the blade housing groove 53 is shortened. This makes it possible to reduce the moment that the rear end 45B of the blade 45 receives due to the force that the tip 45A of the blade 45 receives from the rolling piston rotor.

In addition, it is preferable that the inner diameter Dc of the compression chamber 52 and the length L of the blade are set so as to satisfy, for example, the following (7).
0.2≦L/Dc...(7)
In this manner, by setting the inner diameter Dc of the compression chamber 52 and the length L of the blade so as to satisfy the above formula (7), it is possible to prevent the blade 45 from falling out of the blade accommodating groove 53 .

Moreover, it is preferable that the length L and the thickness t of the blade 45 are set so as to satisfy, for example, the following formula (8).
t/L≦0.5 (8)
In this way, by setting the length L and the thickness t of the blade 45 so as to satisfy the above formula (8), it is possible to prevent the thickness t of the blade 45 from becoming too thin relative to the length L of the blade 45. This makes it possible to prevent the strength of the blade 45 from decreasing.

The maximum protrusion amount Pmax of the blade 45 is preferably set within a range of, for example, 50% to 70% of the length L of the blade 45. Furthermore, the maximum protrusion amount Pmax of the blade 45 is more preferably set within a range of, for example, 60% to 70% of the length L of the blade 45.
For example, if the maximum protrusion amount Pmax of the blade 45 is smaller than 50% of the length of the blade 45, the effect of reducing the outer diameter _R2 of the cylinder 38 is reduced.
On the other hand, if the maximum protrusion amount Pmax of the blade 45 is greater than 70% of the length of the blade 45, the length of the blade 45 accommodated in the blade accommodating groove 53 will be too short, causing the tip 45A side of the blade 45 to oscillate significantly in the circumferential direction of the piston rotor 41.

This may result in poor contact of the tip 45A of the blade 45 with the outer circumferential surface 41a of the piston rotor 41. This may make it difficult to separate the low pressure chamber 52A and the high pressure chamber 52B using the blade 45.
Therefore, by setting the maximum protrusion amount Pmax of the blade 45 within the range of 50% or more and 70% or less of the length L of the blade 45, it is possible to separate the low pressure chamber 52A and the high pressure chamber 52B using the blade 45 while reducing the outer diameter _R2 of the cylinder 38.

The blade pressing member 47 is disposed in a blade accommodating groove 53 located on the rear end 45B side of the blade 45. The blade pressing member 47 is a member for pressing the tip 45A of the blade 45 against the outer circumferential surface 41a of the piston rotor 41.
For example, a blade pressing spring can be used as the blade pressing member 47. In this case, by fixing one end of the blade pressing spring to the rear end 45B of the blade 45 and fixing the other end of the blade pressing spring to the cylinder body 51, it becomes possible to press the tip 45A of the blade 45 against the outer circumferential surface 41a of the piston rotor 41.

In the compression chamber 52 configured as described above, when a gas-phase refrigerant is introduced into the compression chamber 52, the volume of the compression chamber 52 gradually decreases due to the eccentric rotation of the piston rotor 41, and the gas-phase refrigerant is compressed.
When the pressure of the compressed refrigerant increases, a reed valve (not shown) is pushed open and the compressed refrigerant is discharged outside the cylinder 38.
The compressed refrigerant is discharged through a discharge pipe 31 provided at the upper part of the housing 17 into a pipe (not shown) connected to the discharge pipe 31 .

The shaft 24 is accommodated in the housing 17 and has a shaft body 56 and an eccentric shaft portion 39 provided on the shaft body 56 .
The shaft body 56 extends in the Z direction so as to penetrate the compression chamber 52. The axis _O1 coincides with the axis of the housing 17.

The upper bearing 26 is accommodated within the housing 17. The upper bearing 26 is disposed on the upper surface of the cylinder 38 so as to close the upper end (open end) of the compression chamber 52. The upper bearing 26 surrounds the outer circumferential surface of the shaft body 56 located directly above the cylinder 38. The upper bearing 26 supports the shaft body 56 in a state in which the shaft body 56 is rotatable around the axis _O1 .

The lower bearing 27 is accommodated in the housing 17. The lower bearing 27 is disposed on the lower surface of the cylinder 38 so as to close the lower end (open end) of the compression chamber 52. The lower bearing 27 surrounds the outer circumferential surface of the shaft body 56 located directly below the cylinder 38. The lower bearing 27 supports the shaft body 56 in a state in which the shaft body 56 is rotatable around the axis _O1 .

The electric motor 29 has a rotor 61 and a stator 62. The rotor 61 is provided on an upper portion of the shaft body 56.
The stator 62 is disposed on the outer side of the rotor 61. The stator 62 is fixed to the inner circumferential surface of the housing 17.
The electric motor 29 configured as described above electrically drives the compression unit 21 via the shaft 24 .

The discharge pipe 31 is inserted into the through-hole 35A and fixed to the cover 35. The discharge pipe 31 is a pipe for discharging the compressed refrigerant generated by the compression section 21 to the outside. The discharge pipe 31 may be disposed, for example, at a position where the axis _O1 passes.

The accumulator 12 is fixed to the cylindrical portion 33 by fixing means such as welding or bolts via a plate-shaped bracket 13. The accumulator 12 has an intake port 12A at the upper end for drawing in the refrigerant. The accumulator 12 takes in the refrigerant from the intake port 12A and separates the refrigerant into gas and liquid.

One end of the suction pipe 14 reaches the gas phase in the accumulator 12 , and the other end is connected to a refrigerant supply passage 55 that constitutes the compression section 21 .
The suction pipe 14 is inserted into the housing 17 via a guide pipe 18. The suction pipe 14 is fixed to the guide pipe 18.
The suction pipe 14 supplies the gas-phase refrigerant in the accumulator 12 to the compression chamber 52 .

According to the rotary compressor 10 of this embodiment, by setting the length L of the blade 45 and the thickness t of the blade 45 so as to satisfy the above formulas (5) and (6), it is possible to shorten the length L of the blade 45 while setting the thickness t that allows the strength of the blade 45 to be maintained.

In this manner, by shortening the length L of the blade 45 and setting the thickness t at which the strength of the blade 45 can be maintained, it is possible to prevent a decrease in the strength of the blade 45 .
Furthermore, by shortening the length L of the blade 45, it is possible to reduce the outer diameter _R2 of the cylinder 38, so that the outer diameter of the rotary compressor 10 (the outer diameter of the housing 17 (the cylindrical portion 33)) can be reduced.

In addition, by shortening the length L of the blade 45, the distance from the position of the blade 45 where the blade 45 intersects with the inner circumferential surface 52a of the compression chamber 52 (hereinafter referred to as the "fulcrum") to the rear end 45B of the blade 45 housed in the blade housing groove 53 is shortened. This makes it possible to reduce the moment that the rear end 45B of the blade 45 receives due to the force that the tip 45A of the blade 45 receives from the rolling piston rotor.

Although the preferred embodiment of the present invention has been described in detail above, the present invention is not limited to such a specific embodiment, and various modifications and variations are possible within the scope of the gist of the present invention as described in the claims.

In this embodiment, the case where one compression section 21 is provided in the _direction of the axis O1 has been described as an example, but the present invention is also applicable to a rotary compressor in which a plurality of compression sections are provided in the direction of the axis _O1 .

DESCRIPTION OF SYMBOLS 10...Rotary compressor 11...Compressor body 12...Accumulator 12A...Suction port 13...Bracket 14...Suction pipe 14A...Tip portion 17...Housing 18...Guide pipe 21...Compression portion 24...Shaft 26...Upper bearing 27...Lower bearing 29...Motor-driven portion 31...Discharge pipe 33...Cylindrical portion 33A...Suction hole 33a, 52a...Inner peripheral surface 34...Bottom portion 35...Cover portion 35A...Penetration portion 38...Cylinder 39...Eccentric shaft portion 41...Piston rotor 41a...Outer peripheral surface 45...Blade 45a, 45b...Side surface 45A...Tip portion 45B...Rear end 45C...Blade body 45Ca...Surface 45D...Hard coating 47...Blade pressing member 51...Cylinder body 52...Compression chamber 52A...Low-pressure chamber 52B: High pressure chamber 53: Blade receiving groove 55: Coolant supply passage 56: Shaft body 61: Rotor 62: Stator A: Internal space Dc: Inner diameter L, Ls: Length _O1 , _O2 : Axis P1: External force P2: Reaction force Pmax: Maximum protrusion amount t: Thickness _R1 , _R2 : Outer diameter

Claims (1)

a cylinder having a cylinder body accommodated in a housing, a cylindrical compression chamber formed in the cylinder body, and a blade accommodating groove formed in the cylinder body, communicating with the compression chamber, and extending from an inner peripheral surface of the compression chamber to a radially outward direction of the cylinder body;
an upper bearing disposed on an upper surface of the cylinder so as to close an upper end of the compression chamber;
a lower bearing disposed on a lower surface of the cylinder so as to close a lower end of the compression chamber;
a shaft that is rotatably supported by the upper bearing and the lower bearing, the shaft body being inserted into the compression chamber, and an eccentric shaft portion that is provided on the shaft body and disposed in the compression chamber;
a piston rotor provided on the outer side of the eccentric shaft portion and rolling along an inner circumferential surface of the compression chamber;
a blade having at least a portion disposed within the blade groove, the blade moving in a radial direction of the cylinder body with a tip disposed on the compression chamber side in contact with an outer circumferential surface of the piston rotor, the blade separating the compression chamber into a low pressure chamber and a high pressure chamber;
a blade pressing member provided in the blade accommodating groove and configured to press a tip of the blade against an outer circumferential surface of the piston rotor;
Equipped with
When the inner diameter of the compression chamber is Dc, the length of the blade in the radial direction of the cylinder body is L, and the thickness of the blade in the circumferential direction of the cylinder body is t, the following formulas (1), (2) , (3) , and (4) are satisfied:
L/Dc≦0.4 (1)
0.2≦t/L...(2)
0.2≦L/Dc...(3)
t/L≦0.5...(4)
The blade has a blade body and a hard coating covering a surface of the blade body,
A rotary compressor in which a maximum value of a blade protruding amount, which is an amount by which the blade protrudes into the compression chamber, is 50% or more and 70% or less of a length L of the blade .

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