JP2020109281A - Rotary compressor - Google Patents

Abstract

To provide a rotary compressor that can be miniaturized in an outer diameter thereof while suppressed in deterioration in strength of a blade.SOLUTION: A rotary compressor satisfies following relations (1) and (2) where Dc represents an inner diameter of a compression chamber 52, L represents a length of a blade 45 in a radial direction of a cylinder body 51 and t represents a thickness of the blade 45 in a circumferential direction of the cylinder body 51. (1) L/Dc≤0.4, (2) 0.2≤t/L.SELECTED DRAWING: Figure 2

Description

The present invention relates to a rotary compressor.

There is a rotary compressor as one of compressors used in a refrigerating device, an air conditioner, and the like (see, for example, Patent Document 1).
Such a rotary compressor includes a cylinder, a shaft, an upper bearing, a lower bearing, a piston rotor, a blade (vane), and a housing that houses these.

The cylinder has a cylindrical compression chamber and a blade accommodating groove extending in the radial direction. The shaft has a shaft main body penetrating the compression chamber and an eccentric shaft portion provided in the shaft main body and arranged in the compression chamber.
The upper bearing is arranged at the upper end of the cylinder so as to close the upper end of the compression chamber. The lower bearing is arranged at the lower end of the cylinder so as to close the lower end of the compression chamber. The upper bearing and the lower bearing support the shaft body in a rotatable state.

The piston rotor is provided on the outer circumference of the eccentric shaft portion. A part of the outer peripheral surface of the piston rotor is in contact with the inner peripheral surface of the compression chamber. The piston rotor rolls along the inner peripheral surface of the compression chamber.
The blade is arranged in the blade accommodating groove and moves in the radial direction while being in contact with the outer peripheral surface of the piston rotor. The blade separates the compression chamber into a low pressure chamber and a high pressure chamber.

JP, 2018-115566, A

In recent years, from the viewpoint of reducing the outer diameter of the rotary compressor (outer diameter of the housing), it is possible to reduce the outer diameter of the cylinder by reducing the strength of the blade, and the outer diameter of the rotary compression. There is a desire to achieve this.

Therefore, an object of the present invention is to provide a rotary compressor capable of reducing the outer diameter of the rotary compressor while suppressing the reduction in the strength of the blade.

In order to solve the above problems, a rotary compressor according to an aspect of the present invention is formed in a cylinder main body housed in a housing, a cylindrical compression chamber formed in the cylinder main body, and the cylinder main body. A cylinder having a blade accommodating groove that is in communication with the compression chamber and extends radially outward of the cylinder body from the inner peripheral surface of the compression chamber, and is arranged on the upper surface of the cylinder so as to close the upper end of the compression chamber. An upper bearing, a lower bearing disposed on the lower surface of the cylinder so as to close the lower end of the compression chamber, rotatably supported by the upper bearing and the lower bearing, and inserted into the compression chamber. And a shaft provided on the shaft body and having an eccentric shaft portion arranged in the compression chamber, and a shaft provided outside the eccentric shaft portion and rolling along the inner peripheral surface of the compression chamber. And a piston rotor that moves in the radial direction of the cylinder body in a state where at least a part of the piston rotor is arranged in the blade accommodating groove, and the tip arranged on the compression chamber side is in contact with the outer peripheral surface of the piston rotor. A blade that separates the compression chamber into a low-pressure chamber and a high-pressure chamber, and a blade pressing member that is provided in the blade accommodation groove and presses the tip of the blade against the outer peripheral surface of the piston rotor, When the inner diameter of the 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 equations (1) and (2) are given. Meet
L/Dc≦0.4 (1)
0.2≦t/L (2)

According to the present invention, by setting the blade length L and the blade thickness t so as to satisfy the above formula (1) and the above formula (2), the blade length L is shortened and The thickness t can maintain the strength of

For example, if the length of the 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 small, so the force per unit area received by the side surface of the blade is large. Become.
On the other hand, as described above, the length L of the blade is shortened and the thickness t is set so that the strength of the blade can be maintained.
Then, by shortening the length L of the blade, it is possible to reduce the outer diameter of the cylinder, so that the outer diameter of the rotary compressor (outer diameter of the housing) can be reduced.

Further, by shortening the length L of the blade, the distance from the position (fulcrum) of the blade where the blade and the inner peripheral surface of the compression chamber intersect to the rear end of the blade housed in the blade housing groove becomes shorter. As a result, the moment received by the rear end of the blade due to the force received by the tip of the blade from the rolling piston rotor can be reduced.

Further, in the rotary compressor according to the aspect of the present invention, the inner diameter Dc of the compression chamber and the length L of the blade may satisfy the following expression (3).
0.2≦L/Dc (3)

Thus, by setting the inner diameter Dc of the compression chamber and the length L of the blade so as to satisfy the above expression (3), it is possible to prevent the blade from falling out of the blade accommodating groove.

Further, in the rotary compressor according to the aspect of the present invention, the length L of the blade and the thickness t of the blade may satisfy the following expression (4).
t/L≦0.5 (4)

As described above, by setting the blade length L and the blade thickness t so as to satisfy the above formula (4), the blade thickness t becomes too thin with respect to the blade length L. Can be suppressed. This can prevent the strength of the blade from decreasing.

Further, in the rotary compressor according to the aspect of the present invention, the blade may include a blade body and a hard coating that covers a surface of the blade body.

As described above, since the blade has the hard coating that covers the surface of the blade body, the strength of the blade body can be reinforced. Thereby, the strength of the blade can be improved.

In the rotary compressor according to one aspect of the present invention, the maximum value of the blade pop-out amount, which is the amount of the blade popping out into the compression chamber, is 50% or more and 70% or less of the length L of the blade. Good.

For example, when the maximum value of the amount of protrusion of the blade (hereinafter, referred to as “maximum amount of protrusion of blade”) is smaller than 50% of the length of the blade, the effect of reducing the outer diameter of the cylinder becomes small.
On the other hand, if the maximum protrusion amount of the blade is larger than 70% of the length of the blade, the length of the blade accommodated in the blade accommodating groove becomes too short, and the tip side of the blade vibrates greatly in the circumferential direction of the piston rotor. It will be moved.
As a result, the contact state of the tip of the blade with the outer peripheral surface of the piston rotor may deteriorate. Therefore, it may be difficult to separate the low pressure chamber 52A and the high pressure chamber 52B using the blade.
Therefore, by setting the length L of the blade to 50% or more and 70% or less, it is possible to use the blade to separate the low pressure chamber and the high pressure chamber 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 decrease in the strength of the blade.

It is a sectional view showing a schematic structure of a rotary compressor concerning an embodiment of the present invention. It is a sectional view of A ₁ -A ₂ along the line of the rotary compressor shown in FIG. It is sectional drawing which cut|disconnected the blade by the virtual surface orthogonal to the length direction of the blade shown in FIG. 2, and is the figure which saw the cut surface from the B direction.

(Embodiment)
The rotary compressor 10 of the present embodiment will be described with reference to FIGS. 1 to 3. In FIG. 1, O ₁ is the axis of the shaft 24 (hereinafter referred to as “axis O ₁ ”), O ₂ is the axis of the eccentric shaft portion 39 (hereinafter referred to as “axis O ₂ ”), and Z is the height of the rotary compressor 10. Direction (vertical direction).
Further, in FIG. 1, R ₁ is the outer diameter of the housing 17 (cylindrical portion 33) (hereinafter referred to as “outer diameter R ₁ ”), and R ₂ is the outer diameter of the cylinder 38 (hereinafter referred to as “outer diameter R ₂ ”). ) Are shown respectively.

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

The rotary compressor 10 includes 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 unit 21, a shaft 24, an upper bearing 26, a lower bearing 27, an electric unit 29, and a discharge pipe 31.

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

The tubular portion 33 extends in the Z direction, and its upper end and lower end are open ends. A suction hole 33A is formed in the lower portion of the cylindrical portion 33.

The bottom portion 34 is fixed to the tubular portion 33 in a state where the upper portion is inserted into the lower end of the tubular portion 33. Thereby, the bottom portion 34 closes the lower end of the tubular portion 33. The lower portion of the bottom portion 34 projects downward from the lower end of the tubular portion 33.

The lid portion 35 is fixed to the tubular portion 33 with the lower portion inserted into the upper end of the tubular portion 33. The upper portion of the lid portion 35 projects from the upper end of the tubular portion 33.
A penetrating portion 35A is formed in the lid portion 35.

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

The compression unit 21 is housed in the housing 17 and arranged in the lower part of the internal space A.
The compression section 21 includes a cylinder 38, an eccentric shaft section 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 coolant supply passage 55, and a discharge hole (not shown).
A part of the outer peripheral surface of the cylinder body 51 is fixed to the inner peripheral surface 33 a below the tubular portion 33.
The compression chamber 52 is formed so as to penetrate the central portion of the cylinder body 51. The compression chamber 52 has a cylindrical shape and has an inner peripheral surface 52a.

The blade accommodating groove 53 is formed in the cylinder body 51. The blade housing groove 53 communicates with the compression chamber 52, and extends from the inner peripheral surface 52 a of the compression chamber 52 to the radially outer side of the cylinder body 51. Of the end portions of the blade accommodating groove 53, the end portion arranged on the outer peripheral side of the cylinder body 51 is arranged inside the cylinder body 51. That is, the blade accommodating groove 53 does not penetrate the cylinder body 51 in the radial direction.

The coolant supply passage 55 is formed in the cylinder body 51. The coolant supply passage 55 radially penetrates the cylinder body 51 arranged outside the compression chamber 52.
As a result, one end of the refrigerant supply path 55 located on the compression chamber 52 side communicates with the compression chamber 52.
The other end of the coolant supply passage 55 is arranged so as to face the suction hole 33A formed in the tubular portion 33. The other end of the coolant supply passage 55 is shaped so that the tip end portion 14A of the suction pipe 14 can be mounted.
The refrigerant supply path 55 configured as described above guides the gas-phase refrigerant supplied from the suction pipe 14 to the compression chamber 52.

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

The eccentric shaft portion 39 is provided in a portion of the shaft main body 56 that constitutes the shaft 24 and extends in the Z direction and that is inserted into the compression chamber 52. As a result, the eccentric shaft portion 39 is arranged in the compression chamber 52. The eccentric shaft portion 39 has a columnar shape.
The axis O ₂ of the eccentric shaft portion 39 is arranged at a position offset from the axis O ₁ 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 arranged outside the eccentric shaft portion 39 and also in the compression chamber 52. The piston rotor 41 rolls along the inner peripheral surface 52 a of the compression chamber 52 when the eccentric shaft portion 39 rotates.

The blade 45 is a plate-shaped member, and at least a part of the blade 45 is arranged in the blade accommodating groove 53. The blade 45 extends in the same direction as the blade accommodation groove 53 extends.
The blade 45 has a front end 45A, a rear end 45B, and side surfaces 45a and 45b.
The tip 45A is a portion that comes into contact with the outer peripheral surface 41a of the rolling piston rotor 41. The rear end 45B is an end arranged on the side opposite to the front 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 a surface of the compression chamber 52 arranged on the low pressure chamber 52A side. The side surface 45a receives the reaction force P2 when the tip 45A of the blade 45 receives the external force P1. The side surface 45b is a surface arranged on the opposite side of the side surface 45a.

The blade 45 moves in the radial direction of the cylinder body 51 while being in contact with the outer peripheral surface 41 a of the piston rotor 41. In other words, the length of the blade 45 accommodated in the blade accommodating groove 53 (in other words, the protrusion amount of the blade 45 protruding into the compression chamber 52) is changed by the piston rotor 41 rolling.
The blade 45 divides 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 include, for example, a blade body 45C and a hard coating 45D that covers 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, a tungsten carbide film, or the like can be used.

As described above, since the blade 45 has the hard coating 45D that covers the surface 45Ca of the blade body 45C, the strength of the blade body 45C can be reinforced. Thereby, the strength of the blade 45 can be improved.

The length L of the blade 45 and the thickness t of the blade 45 may be set so as to satisfy the following expressions (5) and (6) when 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 formula (5) and the above formula (6), the length L of the blade 45 is shortened. The thickness t can maintain the strength of the blade 45.

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 small, and therefore, the unit area received by the side surface of the blade 45 The power of will increase.
On the other hand, as described above, by shortening the length L of the blade 45 and setting the thickness t so that the strength of the blade 45 can be maintained, it is possible to suppress the decrease in the strength of the blade 45. ..
Then, by shortening the length L of the blade 45, it is possible to reduce the outer diameter R ₂ of the cylinder 38. Therefore, the outer diameter of the rotary compressor 10 (the outer diameter of the housing 17 (cylindrical portion 33)). ) Can be miniaturized.

Further, by shortening the length L of the blade 45, the rear end of the blade 45 housed in the blade housing groove 53 from the position (fulcrum) of the blade 45 where the blade 45 intersects with the inner peripheral surface 52a of the compression chamber 52. The distance to 45B becomes shorter. As a result, 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 can be reduced.

The inner diameter Dc of the compression chamber 52 and the length L of the blade are preferably set so as to satisfy, for example, the following (7).
0.2≦L/Dc (7)
As described above, by setting the inner diameter Dc of the compression chamber 52 and the length L of the blade so as to satisfy the above expression (7), it is possible to prevent the blade 45 from falling out of the blade housing groove 53.

Further, it is preferable that the length L of the blade 45 and the thickness t of the blade 45 be set so as to satisfy the following expression (8), for example.
t/L≦0.5 (8)
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 expression (8), the thickness t of the blade 45 with respect to the length L of the blade 45 is It is possible to prevent the film from becoming too thin. This can 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 50% or more and 70% or less of the length L of the blade 45, for example. Further, the maximum protrusion amount Pmax of the blade 45 is more preferably set within a range of 60% or more and 70% or less of the length L of the blade 45, for example.
For example, when 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 R ₂ of the cylinder 38 becomes small.
On the other hand, if the maximum protrusion amount Pmax of the blade 45 is larger than 70% of the length of the blade 45, the length of the blade 45 accommodated in the blade accommodating groove 53 becomes too short. The rotor 41 is greatly swung in the circumferential direction.

As a result, the contact state of the tip 45A of the blade 45 with the outer peripheral surface 41a of the piston rotor 41 may deteriorate. Therefore, it may be 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, the low pressure chamber 52A and the high pressure chamber 52B are separated by using the blade 45. The outer diameter R ₂ of the cylinder 38 can be reduced.

The blade pressing member 47 is arranged in the blade housing 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 end 45A of the blade 45 against the outer peripheral surface 41a of the piston rotor 41.
As the blade pressing member 47, for example, a blade pressing spring can be used. 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, the tip 45A of the blade 45 is pressed against the outer peripheral surface 41a of the piston rotor 41. It is possible to guess.

In the compression chamber 52 configured as described above, when the vapor-phase refrigerant is introduced into the compression chamber 52, the volume of the compression chamber 52 is gradually reduced by the eccentric rolling of the piston rotor 41, and the vapor-phase refrigerant is compressed. It
When the pressure of the compressed refrigerant increases, the reed valve (not shown) is pushed open, and the compressed refrigerant is discharged to the outside of the cylinder 38.
The compressed refrigerant is discharged into a pipe (not shown) connected to the discharge pipe 31 via the discharge pipe 31 provided in the upper portion of the housing 17.

The shaft 24 is housed in the housing 17, and has a shaft main body 56 and an eccentric shaft portion 39 provided on the shaft main body 56.
The shaft body 56 extends in the Z direction so as to penetrate the compression chamber 52. The axis O ₁ coincides with the axis of the housing 17.

The upper bearing 26 is housed in the housing 17. The upper bearing 26 is arranged 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 peripheral surface of the shaft body 56 located immediately above the cylinder 38. The upper bearing 26 supports the shaft body 56 in a state where the shaft body 56 is rotatable about the axis O ₁ .

The lower bearing 27 is housed in the housing 17. The lower bearing 27 is arranged 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 peripheral surface of the shaft main body 56 located immediately below the cylinder 38. The lower bearing 27 supports the shaft body 56 in a state where the shaft body 56 can rotate around the axis O ₁ .

The electric part 29 includes a rotor 61 and a stator 62. The rotor 61 is provided above the shaft body 56.
The stator 62 is arranged outside the rotor 61. The stator 62 is fixed to the inner peripheral surface of the housing 17.
The electric section 29 configured as described above electrically drives the compression section 21 via the shaft 24.

The discharge pipe 31 is fixed to the lid portion 35 while being inserted into the penetrating portion 35A. The discharge pipe 31 is a pipe for leading the compressed refrigerant generated by the compression unit 21 to the outside. The discharge pipe 31 may be arranged at a position where the axis O ₁ passes, for example.

The accumulator 12 is fixed to the tubular portion 33 by means of fixing means such as welding or bolts via a plate-shaped bracket 13. The accumulator 12 has a suction port 12A at the upper end for sucking the refrigerant. The accumulator 12 takes in a refrigerant from the suction 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 the refrigerant supply passage 55 forming the compression unit 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 vapor phase refrigerant in the accumulator 12 to the compression chamber 52.

According to the rotary compressor 10 of the present embodiment, by setting the length L of the blade 45 and the thickness t of the blade 45 so as to satisfy the expressions (5) and (6), After shortening the length L, it becomes possible to make the thickness t capable of maintaining the strength of the blade 45.

As described above, the length L of the blade 45 is shortened and the thickness t is set so that the strength of the blade 45 can be maintained.
Then, by shortening the length L of the blade 45, it is possible to reduce the outer diameter R ₂ of the cylinder 38. Therefore, the outer diameter of the rotary compressor 10 (the outer diameter of the housing 17 (cylindrical portion 33)). ) Can be miniaturized.

Further, by shortening the length L of the blade 45, the blade 45 is housed in the blade housing groove 53 from the position of the blade 45 where the blade 45 intersects with the inner peripheral surface 52a of the compression chamber 52 (hereinafter referred to as “fulcrum”). The distance to the rear end 45B of the blade 45 becomes shorter. As a result, 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 can be reduced.

Although the preferred embodiments of the present invention have been described in detail above, the present invention is not limited to such specific embodiments, and various modifications are possible within the scope of the gist of the present invention described in the claims. It can be modified and changed.

In the present embodiment has been described taking a case in which a single compression unit 21 in the axial O ₁ direction as an example, also applicable to a rotary compressor provided with a plurality of compression portions in the axial O ₁ direction is there.

DESCRIPTION OF SYMBOLS 10... Rotary compressor 11... Compressor main body 12... Accumulator 12A... Suction port 13... Bracket 14... Suction pipe 14A... Tip part 17... Housing 18... Guide pipe 21... Compression part 24... Shaft 26... Upper bearing 27... Lower bearing 29... Electric part 31... Discharge pipe 33... Cylindrical part 33A... Suction hole 33a, 52a... Inner peripheral surface 34... Bottom part 35... Lid part 35A... Penetration part 38... Cylinder 39... Eccentric shaft part 41... Piston rotor 41a... Outer circumference Surface 45... Blade 45a, 45b... Side surface 45A... Tip 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 accommodation groove 55... Refrigerant supply path 56... Shaft body 61... Rotor 62... Stator A... Internal space Dc... Inner diameter L, Ls... Length O ₁ , O ₂ ... Axis P1... External force P2... Reaction force Pmax... Maximum protrusion amount t...thickness R ₁ , R ₂ ... outer diameter

Claims (5)

A cylinder body housed in a housing, a cylindrical compression chamber formed in the cylinder body, and a cylinder body formed in the cylinder body and communicating with the compression chamber, and the cylinder body from the inner peripheral surface of the compression chamber. A cylinder having a blade housing groove extending radially outward of
An upper bearing arranged on the upper surface of the cylinder so as to close the upper end of the compression chamber,
A lower bearing arranged on the lower surface of the cylinder so as to close the lower end of the compression chamber,
A shaft body that is rotatably supported by the upper bearing and the lower bearing and that is inserted into the compression chamber; and a shaft that is provided in the shaft body and that has an eccentric shaft portion that is disposed in the compression chamber. ,
A piston rotor provided outside the eccentric shaft portion and rolling along the inner peripheral surface of the compression chamber;
At least a part of which is arranged in the blade accommodating groove, and the tip arranged on the side of the compression chamber is moved in the radial direction of the cylinder body while being in contact with the outer peripheral surface of the piston rotor, and the compression chamber is moved. A blade that separates the low pressure chamber and the high pressure chamber
A blade pressing member which is provided in the blade housing groove and presses the tip of the blade against the outer peripheral 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 equation (1) and the following (2) ) A rotary compressor that satisfies the formula.
L/Dc≦0.4 (1)
0.2≦t/L (2) The rotary compressor according to claim 1, wherein an inner diameter Dc of the compression chamber and a length L of the blade satisfy the following expression (3).
0.2≦L/Dc (3) The rotary compressor according to claim 1 or 2, wherein a length L of the blade and a thickness t of the blade satisfy the following expression (4).
t/L≦0.5 (4) The rotary compressor according to any one of claims 1 to 3, wherein the blade includes a blade body and a hard coating that covers a surface of the blade body. The rotary compressor according to claim 1 or 2, wherein a maximum value of the amount of protrusion of the blade, which is the amount of protrusion of the blade into the compression chamber, is 50% or more and 70% or less of the length L of the blade.

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