WO2021260759A1

WO2021260759A1 - Rotary compressor

Info

Publication number: WO2021260759A1
Application number: PCT/JP2020/024342
Authority: WO
Inventors: 博之山田
Original assignee: 三菱電機株式会社
Priority date: 2020-06-22
Filing date: 2020-06-22
Publication date: 2021-12-30
Also published as: JP7313560B2; JPWO2021260759A1; CN115698508A

Abstract

The present invention discloses a rotary compressor including: a cylinder in which a cylinder chamber is formed; a rolling piston that performs eccentric rotation motion inside the cylinder chamber; a vane of which a first end section is in contact with an outer circumferential surface of the rolling piston to partition the cylinder chamber; and a spring that is stored in a spring storage chamber and that presses a second end section of the vane that is an end section opposite from the first end section, toward the rolling piston. A vane groove that communicates with the cylinder chamber and the spring storage chamber and that slidably holds the vane is formed on the cylinder. On at least one of a facing surface of the vane that faces the vane groove and a facing surface of the vane groove that faces the vane, a first groove of which an internal pressure is increased when the vane moves forward so as to protrude into the cylinder chamber is formed, and a second groove of which one end communicates with the first groove and of which the other end communicates with the spring storage chamber is formed.

Description

Rotary compressor

The present disclosure relates to a rotary compressor in which a cylinder chamber formed in a cylinder is divided into a suction chamber and a compression chamber by a vane.

There is a rotary compressor as one of the refrigerant compressors installed in air conditioners and refrigeration equipment. The compression mechanism of the rotary compressor includes a cylinder, a rolling piston, a vane, and a spring. A cylinder chamber having a substantially cylindrical shape is formed in the cylinder. Further, the cylinder is formed with a vane groove in which one end communicates with the cylinder chamber and the other end communicates with the spring storage chamber in which the spring is stored. The rolling piston is housed in the cylinder chamber of the cylinder. Further, the rolling piston is attached to the eccentric portion of the drive shaft. Therefore, when the drive shaft rotates, the rolling piston eccentrically rotates in the cylinder chamber.

The vane is slidably held in the vane groove of the cylinder. Further, the first end portion of the vane is in contact with the outer peripheral surface of the rolling piston. In addition, the vane slides in the vane groove following the rolling piston that rotates eccentrically in the cylinder chamber, and the first end of the vane is prevented from separating from the outer peripheral surface of the rolling piston. The second end, which is the end opposite to the portion, is pushed toward the rolling piston by a spring. As a result, the cylinder chamber is divided into a suction chamber and a compression chamber by a vane. In other words, the space surrounded by the inner peripheral surface of the cylinder chamber and the outer peripheral surface of the rolling piston is divided into a suction chamber and a compression chamber by a vane. Then, the rolling piston moves eccentrically in the cylinder chamber due to the rotation of the drive shaft, so that the rotary compressor simultaneously sucks the refrigerant into the suction chamber and compresses the refrigerant in the compression chamber.

Here, when the rolling piston approaches the vane groove, the vane is pushed by the rolling piston and is stored in the vane groove while sliding in the vane groove. Therefore, when the vane is retracted into the cylinder chamber, the first end portion of the vane does not separate from the outer peripheral surface of the rolling piston.

On the other hand, when the rolling piston separates from the vane groove, the vane protrudes into the cylinder chamber while sliding in the vane groove due to the force pushed toward the rolling piston side by the spring. This prevents the first end of the vane from moving away from the outer peripheral surface of the rolling piston when the vane protrudes into the cylinder chamber. For this reason, if the frictional force between the vane and the vane groove is large, the vane cannot follow the rolling piston when the vane advances, and the vane separation occurs in which the first end portion of the vane and the outer peripheral surface of the rolling piston are separated from each other. May be done. When this vane separation occurs, noise occurs when the first end of the vane and the outer peripheral surface of the rolling piston recontact each other, and the performance of the rotary compressor deteriorates due to the communication between the suction chamber and the compression chamber. Occurs.

Therefore, a conventional rotary compressor has been proposed in which the frictional force between the vane and the vane groove is reduced (see Patent Document 1). Specifically, in the rotary compressor described in Patent Document 1, a fine recess is formed in the sliding surface of the vane with the vane groove or the sliding surface of the vane with the vane, and the vane and the vane groove are formed. We are trying to reduce the frictional force between them.

International Publication No. 2013-005394

When using a rotary compressor, metal powder is generated due to friction between the vanes and the vane grooves. Further, in the rotary compressor, a sliding portion is present at a position other than between the vane and the vane groove. When a rotary compressor is used, metal powder is also generated from sliding portions other than between the vane and the vane groove. Further, in the rotary compressor, a product is also generated by the reaction between the refrigerant and the refrigerating machine oil. For this reason, in a conventional rotary compressor that reduces the frictional force between the vane and the vane groove, if the rotary compressor is used for a long period of time, the above-mentioned metal powder and products will be vanes and vanes. It invades between the groove and accumulates in the vane or the fine recess formed in the vane groove. As a result, in the conventional rotary compressor that aims to reduce the frictional force between the vane and the vane groove, if the rotary compressor is used for a long period of time, the frictional force between the vane and the vane groove is reduced. There is a problem that the reduction effect is reduced and vane separation occurs.

The present disclosure has been made to solve the above-mentioned problems, and an object thereof is to obtain a rotary compressor capable of suppressing vane separation for a longer period of time than before.

The rotary compressor according to the present disclosure includes a cylinder in which a cylinder chamber is formed, a rolling piston housed in the cylinder chamber and eccentrically rotating in the cylinder chamber, and a first end portion in contact with the outer peripheral surface of the rolling piston. A vane that divides the cylinder chamber into a suction chamber and a compression chamber, and a second end portion of the vane that is housed in a spring storage chamber and is opposite to the first end portion of the vane toward the rolling piston. A vane groove is formed in the cylinder, one end of which communicates with the cylinder chamber and the other end of which communicates with the spring storage chamber, and the vane is slidably held in the vane groove. The vane protrudes into the cylinder chamber on at least one of the surface facing the vane groove in the vane and the surface facing the vane in the vane groove. At least one first groove is formed in which the internal pressure increases when advancing, and at least one second groove is formed in which one end communicates with the first groove and the other end communicates with the spring storage chamber. There is.

In the rotary compressor according to the present disclosure, the contact between the vane and the vane groove can be suppressed by the increasing pressure in the first groove when the vane advances, and the frictional force between the vane and the vane groove can be reduced. can. Further, in the rotary compressor according to the present disclosure, the metal powder and the product that have entered between the vane and the vane groove can be discharged from between the vane and the vane groove by the second groove. Therefore, in the rotary compressor according to the present disclosure, it is possible to suppress the accumulation of metal powder and products that have entered between the vanes and the vane grooves in the first groove. Therefore, the rotary compressor according to the present disclosure can suppress vane separation for a longer period than before.

It is a vertical sectional view which shows the rotary compressor which concerns on Embodiment 1. It is a top view for demonstrating the compression mechanism part of the rotary compressor which concerns on Embodiment 1. FIG. It is a figure which observed the vane of the rotary compressor which concerns on this Embodiment 1 from the first side surface. FIG. 3 is a cross-sectional view taken along the line AA of FIG. It is a figure for demonstrating the operation at the time of advancing the vane of the rotary compressor which concerns on Embodiment 1. It is a figure for demonstrating the operation at the time of retreating of the vane of the rotary compressor which concerns on Embodiment 1. It is a top view for demonstrating the compression mechanism part of the rotary compressor which concerns on Embodiment 2. It is a top view for demonstrating the compression mechanism part of the rotary compressor which concerns on Embodiment 2. It is a figure which observed the vane of the rotary compressor which concerns on Embodiment 2 from the first side surface. It is a figure which observed the vane of the rotary compressor which concerns on Embodiment 2 from the 2nd side surface. It is a top view which shows an example of the vane of the rotary compressor which concerns on Embodiment 2. It is a figure which observed the vane of the rotary compressor which concerns on this Embodiment 3 from the first side surface. 12 is a cross-sectional view taken along the line BB of FIG. It is a figure which observed an example of the vane of the rotary compressor which concerns on this Embodiment 4 from the first side surface. It is a figure which observed an example of the vane of the rotary compressor which concerns on this Embodiment 4 from the first side surface. It is a figure which observed an example of the vane of the rotary compressor which concerns on this Embodiment 4 from the first side surface. It is a figure which observed an example of the vane of the rotary compressor which concerns on this Embodiment 4 from the first side surface. It is a figure which observed an example of the vane of the rotary compressor which concerns on this Embodiment 4 from the first side surface. It is a figure which observed an example of the vane of the rotary compressor which concerns on this Embodiment 4 from the first side surface. It is a figure which observed the vane of the rotary compressor which concerns on this Embodiment 5 from the first side surface. FIG. 20 is a sectional view taken along the line CC of FIG. It is a figure which observed another example of the vane of the rotary compressor which concerns on Embodiment 5 from the 1st side.

Embodiment 1.
FIG. 1 is a vertical sectional view showing a rotary compressor according to the first embodiment. Further, FIG. 2 is a plan view for explaining the compression mechanism portion of the rotary compressor according to the first embodiment. Note that FIG. 2 is a view of the compression mechanism portion 20 in a state where the upper bearing portion 31, which will be described later, is observed from above in order to facilitate understanding of the internal structure of the compression mechanism portion 20.
The rotary compressor 100 according to the first embodiment includes an electric motor 10, a compression mechanism unit 20, and a drive shaft 60. The drive shaft 60 connects the electric motor 10 and the compression mechanism unit 20. Further, the rotary compressor 100 according to the first embodiment includes a closed container 1. The electric motor 10, the compression mechanism portion 20, and the drive shaft 60 are housed in the closed container 1. Further, in the lower part of the closed container 1, refrigerating machine oil for lubrication of the sliding portion of the compression mechanism portion 20 and the like is stored.

The electric motor 10 includes a stator 11 fixed to the closed container 1 and a rotor 12 that is rotated by the magnetic force generated by the stator 11.

The drive shaft 60 is connected to the rotor 12 of the electric motor 10 and the compression mechanism unit 20, and transmits the driving force of the electric motor 10 to the compression mechanism unit 20. The drive shaft 60 includes a spindle portion 61 and an eccentric portion 62 provided in the middle of the spindle portion 61. The spindle portion 61 and the eccentric portion 62 each have a cylindrical shape. Further, the central axis of the eccentric portion 62 is eccentric with respect to the central axis of the main shaft portion 61. That is, when the spindle portion 61 rotates, the eccentric portion 62 rotates eccentrically. The spindle portion 61 is fixed to the rotor 12 of the electric motor 10. A cylindrically shaped rolling piston 30 is slidably attached to the outer peripheral portion of the eccentric portion 62. The rolling piston 30 is a component of the compression mechanism unit 20.

The compression mechanism unit 20 compresses the low-pressure refrigerant sucked into the compression mechanism unit 20 by the driving force of the electric motor 10 transmitted from the drive shaft 60, and discharges the high-pressure refrigerant into the closed container 1. The compression mechanism portion 20 includes a cylinder 21, a rolling piston 30, a vane 40, an upper bearing portion 31, a lower bearing portion 32, and a spring 34.

The cylinder 21 has a cylindrical cylinder chamber 22 formed inside. The cylinder chamber 22 is divided into a suction chamber 23 and a compression chamber 24 by a vane 40. The central axis of the cylinder chamber 22 is arranged coaxially with the central axis of the main shaft portion 61 of the drive shaft 60. Further, the rolling piston 30 is housed in the cylinder chamber 22. Therefore, as the drive shaft 60 rotates, the eccentric portion 62 and the rolling piston 30 eccentrically rotate with respect to the central axis of the cylinder chamber 22 in the cylinder chamber 22. The upper opening of the cylinder chamber 22 is closed by the upper bearing portion 31. The lower opening of the cylinder chamber 22 is closed by the lower bearing portion 32. Further, the upper bearing portion 31 and the lower bearing portion 32 rotatably support the spindle portion 61 of the drive shaft 60.

A vane groove 27 is formed in the cylinder 21 along the radial direction of the cylinder 21. One end of the vane groove 27 communicates with the cylinder chamber 22. The other end of the vane groove 27 communicates with the spring storage chamber 33 in which the spring 34 is stored. The vane 40 is slidably held in the vane groove 27. In the first embodiment, the spring storage chamber 33 is formed in the cylinder 21. However, the spring storage chamber 33 may be formed outside the cylinder 21, such as between the cylinder 21 and the closed container 1.

The spring 34 stored in the spring storage chamber 33 pushes the second end portion 42 of the vane 40 toward the rolling piston 30. As a result, even if the eccentric portion 62 and the rolling piston 30 move eccentrically in the cylinder chamber 22, the first end portion 41, which is the end portion of the vane 40 opposite to the second end portion 42, is moved to the rolling piston 30. Can be in contact with the outer peripheral surface of. That is, even if the eccentric portion 62 and the rolling piston 30 move eccentrically in the cylinder chamber 22, the cylinder chamber 22 can be partitioned into the suction chamber 23 and the compression chamber 24 by the vane 40. In other words, even if the eccentric portion 62 and the rolling piston 30 move eccentrically in the cylinder chamber 22, the space surrounded by the inner peripheral surface of the cylinder chamber 22 and the outer peripheral surface of the rolling piston is created by the vane 40 with the suction chamber 23. It can be partitioned into a compression chamber 24.

In the following, among the facing surfaces of the vane 40 with the vane groove 27, the facing surface on the compression chamber 24 side is referred to as the first side surface 43. Of the surfaces facing the vane groove 27 in the vane 40, the surface facing the suction chamber 23 is referred to as the second side surface 44. That is, the first side surface 43 and the second side surface 44 are facing surfaces of the vane 40 with the vane groove 27. Further, of the facing surfaces of the vane groove 27 with the vane 40, the facing surface on the compression chamber 24 side is designated as the first wall surface 28. Of the surfaces facing the vane 40 in the vane groove 27, the surface facing the suction chamber 23 is referred to as a second wall surface 29. That is, the first wall surface 28 and the second wall surface 29 are facing surfaces of the vane groove 27 with the vane 40.

Further, the cylinder 21 is formed with a suction port 25 that communicates with the suction chamber 23. One end of the suction pipe 2 is connected to the suction port 25. The other end of the suction pipe 2 is connected to the suction muffler 101. Further, the cylinder 21 is formed with a discharge port 26 that communicates with the compression chamber 24. The discharge port 26 also communicates with the inside of the closed container 1 via a discharge port (not shown) formed in the upper bearing portion 31.

When the rotor 12 of the motor 10 rotates, the drive shaft 60 connected to the rotor 12 also rotates. As a result, in the cylinder chamber 22, the eccentric portion 62 of the drive shaft 60 and the rolling piston 30 attached to the eccentric portion 62 perform an eccentric rotational movement with respect to the central axis of the cylinder chamber 22. When the rolling piston 30 moves eccentrically in the cylinder 21, the volume of the suction chamber 23 expands. As a result, the low-pressure refrigerant flows from the outside of the rotary compressor 100 into the suction chamber 23 through the suction muffler 101, the suction pipe 2, and the suction port 25. When the rolling piston 30 further eccentrically rotates in the cylinder 21, the suction chamber 23 and the suction port 25 do not communicate with each other. At this time, the space that was the suction chamber 23 becomes the compression chamber 24.

On the other hand, when the rolling piston 30 moves eccentrically in the cylinder 21, the volume of the compression chamber 24 shrinks. As a result, the refrigerant in the compression chamber 24 is compressed into a high-pressure refrigerant, which is discharged into the closed container 1 through the discharge port 26 and the discharge port (not shown) of the upper bearing portion 31. The high-pressure refrigerant discharged into the closed container 1 flows out to the outside of the rotary compressor 100 through the discharge pipe 3 communicating with the inside of the closed container 1. When the rolling piston 30 further eccentrically rotates in the cylinder 21, the compression chamber 24 and the discharge port 26 do not communicate with each other. At this time, the space that was the compression chamber 24 becomes the suction chamber 23.

While the rotary compressor 100 is being driven, the vane 40 is housed in the vane groove 27 while sliding in the vane groove 27 and protruding into the cylinder chamber 22 while sliding in the vane groove 27. Repeat the retreat movement. Specifically, when the rolling piston 30 moves away from the vane groove 27, the vane 40 advances due to the force pushed toward the rolling piston 30 by the spring 34. Further, when the rolling piston 30 approaches the vane groove 27, the vane 40 is pushed by the rolling piston 30 and retracts. Further, while the rotary compressor 100 is being driven, the refrigerating machine oil stored in the lower part of the closed container 1 is supplied between the vane 40 and the vane groove 27 via an oil supply passage (not shown).

By the way, in the conventional general rotary compressor, the surface facing the vane groove in the vane is a flat surface. Further, in the conventional general rotary compressor, the surface facing the vane in the vane groove is also a flat surface. In such a conventional general rotary compressor, when the rotary compressor 100 is driven, the frictional force between the vane and the vane groove increases due to the contact between the vane and the vane groove, and the first end portion of the vane In some cases, vane separation may occur in which the outer peripheral surface of the rolling piston is separated from the outer peripheral surface. Specifically, when the vane retracts, the vane is pushed by the rolling piston 30, so that vane separation does not occur. On the other hand, when the vane moves forward due to the pressing force of the spring, if the frictional force between the vane and the vane groove is large, the vane cannot follow the rolling piston and vane separation occurs.

Therefore, in the rotary compressor 100 according to the first embodiment, the vane 40 is configured as follows in order to suppress the occurrence of vane separation when the vane 40 is advanced.

FIG. 3 is a view of the vane of the rotary compressor according to the first embodiment observed from the first side surface. FIG. 4 is a sectional view taken along the line AA of FIG.
In the vane 40 according to the first embodiment, the first side surface 43 and the second side surface 44, which are the surfaces facing the vane groove 27, are substantially flat surfaces. However, unlike the vanes of a conventional general rotary compressor, at least one first groove 51 is formed on the first side surface 43 of the vane 40 according to the first embodiment, and at least one. The second groove 52 is formed. Further, on the second side surface 44 of the vane 40 according to the first embodiment, at least one first groove 51 is formed and at least one second groove 52 is formed, similarly to the first side surface 43. It is formed. That is, in the first side surface 43 and the second side surface 44 of the vane 40, the flat portion 53 is the range in which the first groove 51 and the second groove 52 are not formed. In the vane groove 27 according to the first embodiment, the first wall surface 28 and the second wall surface 29 facing the vane 40 are flat like the vane groove of a conventional general rotary compressor. It is a face.

Specifically, the first groove 51 is a groove in which the internal pressure increases when the vane 40 advances. The first groove 51 includes a convex portion 51a that protrudes from the first end portion 41 toward the second end portion 42. In the first embodiment, the convex portion 51a has a shape in which two linear grooves are communicated with each other at the top portion 51b. A plurality of first grooves 51 may be formed on the first side surface 43 and the second side surface 44. In this case, the pitch P between the first grooves 51 may be an equal pitch or an unequal pitch. Here, as will be described later, in the present embodiment, the frictional force between the vane 40 and the vane groove 27 is reduced by increasing the pressure in the first groove 51 when the vane 40 is advanced. Therefore, when a plurality of first grooves 51 are formed, it is preferable that the first grooves 51 are arranged as close as possible. Therefore, in the first embodiment, the groove width ratio, which is the value obtained by dividing the width W of the first groove 51 by the pitch P, is larger than 0 and less than 1.

The end 52a of the second groove 52 communicates with the first groove 51. Further, the end portion 52b of the second groove 52 is open to the second end portion 42 of the vane 40 arranged in the spring storage chamber 33. That is, the end portion 52b of the second groove 52 communicates with the spring storage chamber 33. A plurality of second grooves 52 may be formed on the first side surface 43 and the second side surface 44.

Subsequently, the operation of the vane 40 according to the first embodiment will be described.

FIG. 5 is a diagram for explaining the operation of the vane of the rotary compressor according to the first embodiment when moving forward. FIG. 6 is a diagram for explaining the operation of the rotary compressor according to the first embodiment when the vane is retracted. The white arrows in FIGS. 5 and 6 indicate the traveling direction of the vane 40. The black arrow at the tip shown in FIGS. 5 and 6 indicates the flow of refrigerating machine oil in the first groove 51 and the second groove 52.

As described above, the refrigerating machine oil is supplied between the vane 40 and the vane groove 27 while the rotary compressor 100 is being driven. The refrigerating machine oil supplied between the vane 40 and the vane groove 27 moves together with the vane 40 due to the viscosity of the refrigerating machine oil. Therefore, as shown in FIG. 5, when the vane 40 is advanced, the refrigerating machine oil flows from the end portion 51c toward the top portion 51b in the convex portion 51a of the first groove 51. As a result, the refrigerating machine oil flowing through the two grooves forming the convex portion 51a joins at the top portion 51b, and the pressure at the position of the top portion 51b increases. Then, since the oil film pressure at the flat portion 53 around the top 51b is secured by the pressure of the top 51b, the first side surface 43 of the vane 40 rises from the first wall surface 28 of the vane groove 27, and the first wall surface 43 is raised. Contact with 28 is suppressed. Similarly, since the pressure of the top 51b secures the oil film pressure at the flat portion 53 around the top 51b, the second side surface 44 of the vane 40 rises from the second wall surface 29 of the vane groove 27, and the second side surface 44 rises from the second wall surface 29. 2 Contact with the wall surface 29 is suppressed. Therefore, in the rotary compressor 100 according to the first embodiment, when the vane 40 is advanced, the frictional force between the vane 40 and the vane groove 27 can be reduced as compared with the conventional general rotary compressor, and the vane can be reduced. It is possible to suppress the occurrence of separation.

Here, also in the conventional rotary compressor, a fine recess is formed in the sliding surface with the vane groove in the vane or the sliding surface with the vane in the vane groove, and the frictional force between the vane and the vane groove is formed. Those aimed at reduction have been proposed. However, in the conventional rotary compressor that aims to reduce the frictional force between the vane and the vane groove, if the rotary compressor is used for a long period of time, the frictional force between the vane and the vane groove is reduced. The effect is reduced and vane separation occurs.

Specifically, when using a rotary compressor, metal powder is generated due to friction between the vanes and the vane grooves. Further, in the rotary compressor, a sliding portion is present at a position other than between the vane and the vane groove. When a rotary compressor is used, metal powder is also generated from sliding portions other than between the vane and the vane groove. Further, in the rotary compressor, a product is also generated by the reaction between the refrigerant and the refrigerating machine oil. For this reason, in a conventional rotary compressor that reduces the frictional force between the vane and the vane groove, if the rotary compressor is used for a long period of time, the above-mentioned metal powder and products will be vanes and vanes. It invades between the groove and accumulates in the vane or the fine recess formed in the vane groove. As a result, in the conventional rotary compressor that aims to reduce the frictional force between the vane and the vane groove, if the rotary compressor is used for a long period of time, the frictional force between the vane and the vane groove is reduced. The reduction effect is reduced, and vane separation occurs.

On the other hand, in the rotary compressor 100 according to the first embodiment, as shown in FIG. 6, when the vane 40 is retracted, the convex portion 51a of the first groove 51 is frozen from the top portion 51b toward the end portion 51c. Machine oil flows. Then, the refrigerating machine oil in the first groove 51 flows into the second groove 52. Further, in the rotary compressor 100 according to the first embodiment, when the vane 40 is retracted, the refrigerating machine oil flows from the end portion 52a to the end portion 52b in the second groove 52. Then, the refrigerating machine oil in the second groove 52 flows out from the end portion 52b to the spring storage chamber 33. Therefore, in the rotary compressor 100 according to the first embodiment, the metal powder and the product that have entered between the vane 40 and the vane groove 27 are moved between the vane 40 and the vane groove 27 by the second groove 52. Can be discharged from. Therefore, in the rotary compressor 100 according to the first embodiment, it is possible to prevent the metal powder and the product that have entered between the vane 40 and the vane groove 27 from accumulating in the first groove 51. Therefore, the rotary compressor 100 according to the first embodiment can suppress the vane separation for a long period of time as compared with the conventional rotary compressor in which the frictional force between the vane and the vane groove is reduced.

In the first embodiment, the first groove 51 and the second groove 52 are formed on the first side surface 43 and the second side surface 44, which are the surfaces facing the vane groove 27 in the vane 40. Not limited to this, the first groove 51 and the second groove 52 may be formed on the first wall surface 28 and the second wall surface 29 which are the surfaces facing the vane 40 in the vane groove 27. Here, as described above, the refrigerating machine oil supplied between the vane 40 and the vane groove 27 moves together with the vane 40. Therefore, when the first groove 51 is formed on the first wall surface 28 and the second wall surface 29, in order to increase the pressure inside the first groove 51 when the vane 40 is advanced, the convex portion 51a is provided at the second end. The shape is such that it protrudes from the portion 42 toward the first end portion 41. As a result, when the vane 40 is advanced, the refrigerating machine oil flows from the end portion 51c toward the top portion 51b in the convex portion 51a of the first groove 51, and the pressure at the position of the top portion 51b can be increased. Further, the first groove 51 and the second groove 52 may be formed on both the surface of the vane 40 facing the vane groove 27 and the surface of the vane groove 27 facing the vane 40. That is, if the first groove 51 and the second groove 52 are formed on at least one of the surface facing the vane groove 27 in the vane 40 and the surface facing the vane 40 in the vane groove 27, the vane is separated for a long period of time. Can be suppressed.

As described above, the rotary compressor 100 according to the first embodiment includes a cylinder 21, a rolling piston 30, a vane 40, and a spring 34. A cylinder chamber 22 is formed in the cylinder 21. The rolling piston 30 is housed in the cylinder chamber 22 and eccentrically rotates in the cylinder chamber 22. In the vane 40, the first end 41 is in contact with the outer peripheral surface of the rolling piston 30, and the cylinder chamber 22 is divided into a suction chamber 23 and a compression chamber 24. The spring 34 is housed in the spring storage chamber 33 and pushes the second end 42, which is the end of the vane 40 opposite to the first end 41, toward the rolling piston 30. The cylinder 21 is formed with a vane groove 27 having one end communicating with the cylinder chamber 22 and the other end communicating with the spring storage chamber 33. The vane 40 is slidably held in the vane groove 27. Then, on at least one of the surface facing the vane groove 27 in the vane 40 and the surface facing the vane 40 in the vane groove 27, the internal pressure increases when the vane 40 protrudes into the cylinder chamber 22 as it advances. At least one first groove 51 is formed, and at least one second groove 52 is formed, one end of which communicates with the first groove 51 and the other end of which communicates with the spring storage chamber 33.

In the rotary compressor 100 configured in this way, as described above, vane separation can be suppressed for a longer period than before.

Embodiment 2.
By making the position of the first groove 51 formed on the surface on the compression chamber 24 side different from the position of the first groove 51 formed on the surface on the suction chamber 23 side as in the second embodiment. , Vane separation can be further suppressed. In the second embodiment, the items not specifically described are the same as those in the first embodiment, and the same functions and configurations as those in the first embodiment are described by using the same reference numerals as those in the first embodiment. ..

7 and 8 are plan views for explaining the compression mechanism portion of the rotary compressor according to the second embodiment. 7 and 8 are views of the compression mechanism portion 20 with the upper bearing portion 31 removed from above. Further, FIG. 7 shows the state in which the vane 40 is most advanced. Further, FIG. 8 shows a state in which the vane 40 is most retracted.

As shown in FIG. 7, when the vane 40 protrudes into the cylinder chamber 22, the difference between the pressure applied to the first side surface 43 from the compression chamber 24 and the pressure applied to the second side surface 44 from the suction chamber 23 causes. The vane 40 is in an inclined posture with respect to the vane groove 27 in a plan view. Therefore, the vane 40 slides in the vane groove 27 in a posture in which the first end portion 41 is tilted toward the suction chamber 23.

Therefore, the gap between the first side surface 43 of the vane 40 and the first wall surface 28 of the vane groove 27 is smaller on the spring storage chamber 33 side and larger on the cylinder chamber 22 side. In other words, the gap between the first side surface 43 of the vane 40 and the first wall surface 28 of the vane groove 27 is smaller on the second end 42 side and larger on the first end 41 side. Therefore, the first side surface 43 of the vane 40 easily comes into contact with the end portion 28a on the first wall surface 28 of the vane groove 27 on the spring storage chamber 33 side. Further, the gap between the second side surface 44 of the vane 40 and the second wall surface 29 of the vane groove 27 is smaller on the cylinder chamber 22 side and larger on the spring storage chamber 33 side. In other words, the gap between the second side surface 44 of the vane 40 and the second wall surface 29 of the vane groove 27 is smaller on the first end 41 side and larger on the second end 42 side. Therefore, the second side surface 44 of the vane 40 is likely to come into contact with the end portion 29a on the cylinder chamber 22 side of the second wall surface 29 of the vane groove 27.

Here, the magnitude of the oil film pressure generated in the gap to which the refrigerating machine oil is supplied is proportional to the cube of the reciprocal of the dimension of the gap. Therefore, in a region where the gap is small, the effect of floating the vane 40 due to the increase in pressure in the first groove 51 can be expected. On the other hand, in the region where the gap is large, the apparent size of the gap is increased by the first groove 51, which causes a decrease in the oil film pressure. Therefore, by arranging the first groove 51 in the region where the gap is small, the contact between the vane 40 and the vane groove 27 can be suppressed more effectively, and the frictional force between the vane 40 and the vane groove 27 can be more effectively suppressed. Can be reduced to. Therefore, in the second embodiment, the vane 40 is configured as shown in FIGS. 9 and 10 below.

FIG. 9 is a view of the vane of the rotary compressor according to the second embodiment observed from the first side surface. FIG. 10 is a view of the vane of the rotary compressor according to the second embodiment observed from the second side surface.
As described above, the gap between the first side surface 43 of the vane 40 and the first wall surface 28 of the vane groove 27 is the gap between the second side surface 44 of the vane 40 and the second wall surface 29 of the vane groove 27. In comparison, the second end 42 side becomes smaller. In other words, the gap between the second side surface 44 of the vane 40 and the second wall surface 29 of the vane groove 27 is the first as compared with the space between the first side surface 43 of the vane 40 and the first wall surface 28 of the vane groove 27. The end 41 side becomes smaller. Therefore, the forming range of the first groove 51 on the first side surface 43 of the vane 40 is closer to the second end portion 42 than the forming range of the first groove 51 on the second side surface 44 of the vane 40. In other words, the forming range of the first groove 51 on the second side surface 44 of the vane 40 is closer to the first end 41 than the forming range of the first groove 51 on the first side surface 43 of the vane 40.

More specifically, the distance between the first groove 51 formed on the second end portion 42 side of the first side surface 43 of the vane 40 and the second end portion 42 is the second most on the second side surface 44 of the vane 40. It is shorter than the distance between the first groove 51 formed on the end portion 42 side and the second end portion 42. Further, the distance between the first groove 51 formed on the first end portion 41 side of the first side surface 43 of the vane 40 and the first end portion 41 is the most first end portion on the second side surface 44 of the vane 40. It is longer than the distance between the first groove 51 formed on the 41 side and the first end portion 41.

By configuring the vane 40 in this way, the first groove 51 can be arranged at a position where the gap becomes small when the vane 40 slides in the vane groove 27. As a result, the contact between the vane 40 and the vane groove 27 can be further suppressed, and the frictional force between the vane 40 and the vane groove 27 can be further reduced.

At the end of the second embodiment, an example of a suitable forming range of the first groove 51 on the first side surface 43 of the vane 40 and an example of a suitable forming range of the first groove 51 on the second side surface 44 of the vane 40. Will be introduced with reference to FIGS. 9 and 10 described above and FIG. 11 described later.

FIG. 11 is a plan view showing an example of a vane of the rotary compressor according to the second embodiment.
As described above, when the vane 40 slides in the vane groove 27, the first side surface 43 of the vane 40 is most likely to come into contact with the end portion 28a on the first wall surface 28 of the vane groove 27 on the spring storage chamber 33 side. Become. Therefore, it is preferable that the first groove 51 is formed on the first side surface 43 of the vane 40 in a range facing the end 28a when the vane 40 slides in the vane groove 27. Further, when the vane 40 slides in the vane groove 27, the second side surface 44 of the vane 40 is most likely to come into contact with the end portion 29a on the cylinder chamber 22 side of the second wall surface 29 of the vane groove 27. Therefore, it is preferable that the first groove 51 is formed on the second side surface 44 of the vane 40 in a range facing the end portion 29a when the vane 40 slides in the vane groove 27.

Specifically, as shown in FIG. 11, when the vane 40 is viewed in a plan view in a state where the vane 40 is most retracted, the direction of passing through the first end portion 41 and the second end portion 42 of the vane 40 is X. The direction. Further, as shown in FIG. 7, the protrusion length in the X direction of the vane 40 from the vane groove 27 in the state where the vane 40 is most advanced is defined as the stroke amount Xst. Further, as shown in FIGS. 7 and 8, the length of the vane groove 27 in the X direction is defined as the vane groove length lvgd. The formation range of the first groove 51 on the first side surface 43 of the vane 40 is defined as lgd. Of the formation range lgd of the first groove 51 on the first side surface 43 of the vane 40, the point on the side of the first end 41 is set as the starting point lgd1. Of the formation range lgd of the first groove 51 on the first side surface 43 of the vane 40, the point on the second end 42 side is defined as the end point lgd2. The formation range of the first groove 51 on the second side surface 44 of the vane 40 is defined as lgs. Of the formation range lgs of the first groove 51 on the second side surface 44 of the vane 40, the point on the side of the first end 41 is set as the starting point lgs1. Of the formation range lgs of the first groove 51 on the second side surface 44 of the vane 40, the point on the second end 42 side is defined as the end point lgs2.

As shown in FIG. 8, in the state where the vane 40 is most retracted, the first side surface 43 of the vane 40 advances from the first end 41 to the second end 42 along the X direction by the vane groove length lvgd. At the position, it faces the end 28a of the vane groove 27. Therefore, the starting point lgd1 of the formation range lgd of the first groove 51 on the first side surface 43 of the vane 40 is a position advanced from the first end portion 41 along the X direction by the vane groove length lvgd to the second end portion 42. Is preferable. Further, as shown in FIG. 7, in the state where the vane 40 is most advanced, the vane 40 is tilted with respect to the vane groove 27, but the first side surface 43 of the vane 40 is roughly in the X direction from the start point lgd1. It faces the end portion 28a of the vane groove 27 at a position advanced along the stroke amount Xst to the second end portion 42. Therefore, it is preferable that the end point lgd2 of the formation range lgd of the first groove 51 on the first side surface 43 of the vane 40 is a position advanced from the start point lgd1 along the X direction by the stroke amount Xst to the second end portion 42. .. By forming the first groove 51 in such a formation range lgd on the first side surface 43 of the vane 40, the end portion 28a most likely to come into contact with the first side surface 43 of the vane 40 when the vane 40 slides is the vane 40. Contact with the first side surface 43 of the above can be further suppressed. Therefore, the frictional force between the vane 40 and the vane groove 27 can be further reduced.

Further, as shown in FIG. 8, in the state where the vane 40 is most retracted, the second side surface 44 of the vane 40 faces the end portion 29a of the vane groove 27 at the position of the first end portion 41. Therefore, it is preferable that the start point lgs1 of the formation range lgs of the first groove 51 on the second side surface 44 of the vane 40 is the position of the first end portion 41. Further, as shown in FIG. 7, in the state where the vane 40 is most advanced, the vane 40 is tilted with respect to the vane groove 27, but the second side surface 44 of the vane 40 is roughly in the X direction from the start point lgs1. It faces the end portion 29a of the vane groove 27 at a position advanced along the stroke amount Xst to the second end portion 42. Therefore, it is preferable that the end point lgs2 of the formation range lgs of the first groove 51 on the second side surface 44 of the vane 40 is a position advanced from the start point lgs1 along the X direction by the stroke amount Xst to the second end portion 42. .. By forming the first groove 51 in such a formation range lgs on the second side surface 44 of the vane 40, the end portion 29a most likely to come into contact with the second side surface 44 of the vane 40 when the vane 40 slides is the vane 40. Contact with the second side surface 44 of the above can be further suppressed. Therefore, the frictional force between the vane 40 and the vane groove 27 can be further reduced.

As described in the first embodiment, the first groove 51 and the second groove 52 may be formed on the first wall surface 28 and the second wall surface 29 which are the facing surfaces of the vane groove 27 with the vane 40. .. At this time, when the first groove 51 is arranged at a position where the gap becomes small when the vane 40 slides in the vane groove 27, the first groove 51 is formed at the following position. Specifically, the distance between the first groove 51 formed on the second end portion 42 side of the first wall surface 28 and the second end portion 42 is set on the second end portion 42 side of the second wall surface 29. It is shorter than the distance between the formed first groove 51 and the second end portion 42. Further, the distance between the first groove 51 formed on the first end portion 41 side of the first wall surface 28 and the first end portion 41 is formed on the first end portion 41 side of the second wall surface 29. It is longer than the distance between the first groove 51 and the first end 41.

Embodiment 3.
By setting the depth of the second groove 52 as in the third embodiment, it becomes easier to discharge the metal powder and the product that have entered between the vane 40 and the vane groove 27, and the vane separation can be performed for a longer period of time. It can be suppressed. In the third embodiment, the items not specifically described are the same as those of the first embodiment or the second embodiment, and the same functions and configurations as those of the first embodiment or the second embodiment are the same as those of the first embodiment or the second embodiment. It will be described using the same reference numerals as those in the second embodiment.

FIG. 12 is a view of the vane of the rotary compressor according to the third embodiment observed from the first side surface. FIG. 13 is a cross-sectional view taken along the line BB of FIG.
As shown in FIGS. 12 and 13, in the third embodiment, the depth of the second groove 52 is deeper than the depth of the first groove 51.

When considering the shear flow of the fluid between two planes, the average flow velocity of the fluid is 1/2 of the slip velocity. Therefore, the flow rate of the fluid flowing between the two planes is the product of the average flow velocity and the cross-sectional area. That is, by increasing the depth of the second groove 52, the flow rate of the refrigerating machine oil in the second groove 52 increases. Further, due to the increase in the flow rate of the refrigerating machine oil in the second groove 52, the inflow amount of the refrigerating machine oil from the first groove 51 to the second groove 52 also increases when the vane 40 retracts, and the refrigerating machine oil in the first groove 51 The flow velocity of is also increased. Therefore, by increasing the depth of the second groove 52, the metal powder and the product that have entered between the vane 40 and the vane groove 27 can be more easily discharged.

In the third embodiment, the depth of the first groove 51 and the depth of the second groove 52 are set as follows. The design gap between the vane 40 and the vane groove 27 is defined as the nominal gap. The depth of the first groove 51 is 0.01 times or more the nominal gap and 10 times or less the nominal gap. Further, the depth of the second groove 52 is larger than the depth of the first groove 51. Here, in the third embodiment, the second groove 52 of the first side surface 43 and the second groove 52 of the second side surface 44 are formed at opposite positions. Therefore, in the third embodiment, the depth of the second groove 52 is less than half the thickness of the vane 40. The thickness of the vane 40 is a dimension in the direction in which the first side surface 43 and the second side surface 44 face each other.

Embodiment 4.
In the first to third embodiments, the convex portion 51a of the first groove 51 has a shape in which two linear grooves are communicated with each other at the top portion 51b. However, such a shape of the convex portion 51a is merely an example. The convex portion 51a can have various shapes as long as the refrigerating machine oil flows toward the top 51b when the vane 40 advances. In the fourth embodiment, some examples of the shape of the convex portion 51a will be introduced. Further, the shape of the second groove 52 shown in the first to third embodiments is only an example. The second groove 52 can have various shapes as long as it communicates with the first groove 51 and the spring storage chamber 33. In the fourth embodiment, some examples of the shape of the second groove 52 will be introduced. In the fourth embodiment, the items not specifically described are the same as those of the first to the third embodiments, and the same functions and configurations as those of the first to third embodiments are carried out. It will be described using the same reference numerals as any of the first to third embodiments of the above.

FIG. 14 is a view of an example of the vane of the rotary compressor according to the fourth embodiment observed from the first side surface.
As shown in FIG. 14, at least a part of the convex portion 51a of the first groove 51 may be a curved groove. Note that FIG. 14 shows an example in which all of the convex portions 51a of the first groove 51 are composed of curved grooves.

FIG. 15 is a view of an example of the vane of the rotary compressor according to the fourth embodiment observed from the first side surface.
In FIG. 14, the curved groove constituting the convex portion 51a of the first groove 51 is a groove having a protruding shape from the first end portion 41 toward the second end portion 42. Not limited to this, as shown in FIG. 15, at least a part of the convex portion 51a of the first groove 51 has a curved shape having a protruding shape from the second end portion 42 toward the first end portion 41. It may be a groove. In addition, in FIG. 15, an example in which all the convex portions 51a of the first groove 51 are formed of curved grooves having a protruding shape from the second end portion 42 toward the first end portion 41. Shows.

FIG. 16 is a view of an example of the vane of the rotary compressor according to the fourth embodiment observed from the first side surface.
When the vane 40 is viewed from the side, the direction perpendicular to the sliding direction of the vane 40 is defined as the width direction of the vane 40. In the case of FIG. 16, the vertical direction of the paper surface is the width direction of the vane 40. The convex portion 51a of the vane 40 described above has a symmetrical shape with respect to a virtual line passing through the center in the width direction of the vane 40 and parallel to the sliding direction of the vane 40. Not limited to this, as shown in FIG. 16, the convex portion 51a of the vane 40 passes through the center in the width direction of the vane 40 and has an asymmetric shape with respect to the virtual line parallel to the sliding direction of the vane 40. May be.

FIG. 17 is a view of an example of the vane of the rotary compressor according to the fourth embodiment observed from the first side surface.
The vane 40 described above was provided with one convex portion 51a. Not limited to this, as shown in FIG. 17, the vane 40 may include a plurality of convex portions 51a. Note that FIG. 17 shows an example in which the two convex portions 51a are arranged side by side in the width direction of the vane 40.

Further, the convex portion 51a of the vane 40 may be a combination of the above configurations.

18 and 19 are views of an example of the vane of the rotary compressor according to the fourth embodiment observed from the first side surface.
As shown in FIGS. 18 and 19, the axis parallel to the sliding direction of the vane 40 when the vane 40 is viewed from the side is defined as the Y axis. When the Y-axis is defined in this way, the above-mentioned second groove 52 is parallel to the Y-axis when the vane 40 is viewed from the side. Not limited to this, as shown in FIGS. 18 and 19, the second groove 52 may be tilted with respect to the Y axis when the vane 40 is viewed from the side. From the viewpoint of facilitating the discharge of metal powder and products, it is preferable that the inclination of the second groove 52 with respect to the Y axis is small. For example, among the angles formed by the Y-axis and the second groove 52, the angle θ, which is the angle extending toward the second end portion 42, is preferably smaller than 45 °.

Of course, at least a part of the second groove 52 may be composed of a curved groove.

Embodiment 5.
In the first to fourth embodiments, the width and depth of the first groove 51 are constant at all positions. Not limited to this, the first groove 51 may have at least one of a width and a depth different depending on the position. In the fifth embodiment, an example of such a first groove 51 will be described. Further, in the first to fourth embodiments, the width and depth of the second groove 52 are constant at all positions. Not limited to this, the second groove 52 may have at least one of a width and a depth different depending on the position. In the fifth embodiment, an example of such a second groove 52 will also be described. In the fifth embodiment, the items not specifically described are the same as those of the first to the fourth embodiments, and the same functions and configurations as those of the first to the fourth embodiments are carried out. It will be described using the same reference numerals as any of the first to fourth embodiments of the above.

FIG. 20 is a view of the vane of the rotary compressor according to the fifth embodiment observed from the first side surface. 21 is a sectional view taken along the line CC of FIG.
As shown in FIGS. 20 and 21, the depth of the convex portion 51a of the first groove 51 according to the fifth embodiment decreases from the end portion 51c toward the top portion 51b. As described above, when the vane 40 is advanced, the refrigerating machine oil flows from the end portion 51c toward the top portion 51b in the convex portion 51a, and the pressure at the position of the top portion 51b increases, so that the vane 40 and the vane groove 27 The frictional force between them can be reduced. At this time, when the cross-sectional area of the groove decreases with respect to the flow direction of the refrigerating machine oil, a higher pressure is generated because the refrigerating machine oil is incompressible. Therefore, by configuring the convex portion 51a of the first groove 51 so that the depth decreases from the end portion 51c toward the top portion 51b, the vane 40 is compared with the case where the depth of the convex portion 51a is constant. The pressure at the position of the top 51b can be further increased when moving forward. Therefore, by configuring the convex portion 51a of the first groove 51 so that the depth decreases from the end portion 51c toward the top portion 51b, the vane is compared with the case where the depth of the convex portion 51a is constant. The frictional force between the 40 and the vane groove 27 can be further reduced.

In the same way, in the second groove 52, when the cross-sectional area increases with respect to the flow direction of the refrigerating machine oil, the refrigerating machine oil easily flows without receiving pressure resistance. Therefore, the depth of the second groove 52 may be increased from the first end portion 41 toward the second end portion 42. As a result, the metal powder and products that have penetrated between the vane 40 and the vane groove 27 can be discharged more than in the case where the depth of the second groove 52 is constant, and the vane separation is suppressed for a longer period of time. be able to.

Note that FIGS. 20 and 21 describe an example in which the depth of the groove constituting the convex portion 51a changes linearly. However, the depth of the groove constituting the convex portion 51a may change in a curved shape or may change in a stepped shape. The method of changing the depth of the second groove 52 is also the same.

FIG. 22 is a view of another example of the vane of the rotary compressor according to the fifth embodiment observed from the first side surface.
The cross-sectional area of the groove can also be changed by changing the width of the groove. Therefore, as shown in FIG. 22, the width of the convex portion 51a of the first groove 51 may decrease from the end portion 51c toward the top portion 51b. Even if the convex portion 51a of the first groove 51 is formed in this way, the cross-sectional area of the convex portion 51a can be reduced from the end portion 51c toward the top portion 51b. Therefore, even if the convex portion 51a of the first groove 51 is configured in this way, the pressure at the position of the top portion 51b is further increased when the vane 40 is advanced, as compared with the case where the width of the convex portion 51a is constant. be able to. Therefore, even if the convex portion 51a of the first groove 51 is configured in this way, the frictional force between the vane 40 and the vane groove 27 can be further reduced as compared with the case where the width of the convex portion 51a is constant. .. Here, both the width and the depth of the convex portion 51a may decrease from the end portion 51c toward the top portion 51b. That is, if at least one of the width and the depth of the convex portion 51a decreases from the end portion 51c toward the top portion 51b, the frictional force between the vane 40 and the vane groove 27 is further reduced. can.

Similarly, the width of the second groove 52 may be increased from the first end portion 41 toward the second end portion 42. As a result, as compared with the case where the width of the second groove 52 is constant, the metal powder and the product that have entered between the vane 40 and the vane groove 27 can be discharged more, and the vane separation can be suppressed for a longer period of time. Can be done. Here, both the width and the depth of the second groove 52 may increase from the first end portion 41 toward the second end portion 42. That is, the second groove 52 can suppress vane separation for a longer period of time if at least one of the width and the depth decreases from the first end 41 to the second end 42. can.

Note that FIG. 22 shows an example in which the width of the groove constituting the convex portion 51a changes linearly. However, the width of the groove constituting the convex portion 51a may change in a curved shape or may change in a stepped shape. The method of changing the width of the second groove 52 is the same.

1 closed container, 2 suction pipe, 3 discharge pipe, 10 motor, 11 stator, 12 rotor, 20 compression mechanism, 21 cylinder, 22 cylinder chamber, 23 suction chamber, 24 compression chamber, 25 suction port, 26 discharge port , 27 vane groove, 28 first wall surface, 28a end part, 29 second wall surface, 29a end part, 30 rolling piston, 31 upper bearing part, 32 lower bearing part, 33 spring storage chamber, 34 spring, 40 vane, 41st 1 end, 42 2nd end, 43 1st side surface, 44 2nd side surface, 51 1st groove, 51a convex part, 51b top, 51c end, 52 2nd groove, 52a end, 52b end, 53 flat part, 60 drive shaft, 61 spindle part, 62 eccentric part, 100 rotary compressor, 101 suction muffler.

Claims

The cylinder in which the cylinder chamber is formed and the cylinder
A rolling piston housed in the cylinder chamber and rotating eccentrically in the cylinder chamber,
A vane whose first end is in contact with the outer peripheral surface of the rolling piston and which divides the cylinder chamber into a suction chamber and a compression chamber.
A spring that is housed in the spring storage chamber and pushes the second end of the vane, which is the end opposite to the first end, toward the rolling piston.
Equipped with
The cylinder is formed with a vane groove in which one end communicates with the cylinder chamber and the other end communicates with the spring storage chamber.
A rotary compressor in which the vane is slidably held in the vane groove.
At least one of the surface facing the vane groove in the vane and the surface facing the vane in the vane groove increases the internal pressure when the vane advances into the cylinder chamber. A rotary compressor in which one first groove is formed and at least one second groove is formed in which one end communicates with the first groove and the other end communicates with the spring storage chamber.
The first groove and the second groove are formed on the surface of the vane facing the vane groove.
The rotary compressor according to claim 1, wherein the first groove includes a convex portion protruding from the first end portion toward the second end portion.
Of the surfaces facing the vane groove in the vane, the facing surface on the compression chamber side is defined as the first side surface.
When the facing surface on the suction chamber side of the facing surface of the vane with the vane groove is the second side surface,
The distance between the first groove formed on the second end side of the first side surface and the second end portion is such that the distance between the first groove and the second end portion is formed on the second end side of the second side surface. Shorter than the distance between the first groove and the second end,
The distance between the first groove formed on the first end side of the first side surface and the first end portion is such that the distance between the first groove and the first end portion is formed on the first end side of the second side surface. The rotary compressor according to claim 2, which is longer than the distance between the first groove and the first end portion.
The first groove and the second groove are formed on the surface of the vane groove facing the vane.
The rotary compressor according to claim 1, wherein the first groove is provided with a convex portion that protrudes from the second end portion toward the first end portion.
Of the surfaces facing the vanes in the vane groove, the facing surface facing the compression chamber is set as the first wall surface.
When the facing surface on the suction chamber side of the facing surface of the vane groove with the vane is the second wall surface,
The distance between the first groove formed on the second end side of the first wall surface and the second end is such that the distance between the first groove and the second end is formed on the second end side of the second wall surface. Shorter than the distance between the first groove and the second end,
The distance between the first groove formed on the first end surface side of the first wall surface and the first end portion is such that the distance between the first groove and the first end portion is formed on the first end portion side of the second wall surface. The rotary compressor according to claim 4, which is longer than the distance between the first groove and the first end portion.
The rotary according to any one of claims 2 to 5, wherein at least one of the width and the depth of the convex portion of the first groove decreases from the end to the top. Compressor.
The rotary compressor according to any one of claims 1 to 6, wherein the depth of the second groove is deeper than the depth of the first groove.
The second aspect is described in any one of claims 1 to 7, wherein at least one of the width and the depth is increased from the first end portion to the second end portion. Rotary compressor.