JPH10148193A - Rotary compressor - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a rotary compressor; improved in the lubricating condition of the sliding part of a roller and a vane (which are the parts of a compressing mechanism being in a severe condition before), and having high reliability and a long life, in the rotaty compressor used in a freezing store, a refrigerator or an air conditioner. SOLUTION: An oil groove 23, for feeding refrigetantor oil to respective sliding parts, is formed on a crank shaft 1 having a crank pin part 11, and the outer periphery of the crank shaft and the crank pin part 11; and the following are provided: a bearing for rotatably supporting the crank shaft, a roller 4 revolving in a cylinder while being driven with the crank pin part 11, a vane 3 wherein part of a tip has an R shape, and a roller groove part 21 having curvature nearly the same as that of the vane 3 tip in the outer peripheral surface of the roller 4; and the vane tip is abuttingly arranged in the roller groove part 21 to provide at least one or more oiling hole 22 communicating with the light load side of the inner peripheral surface of the roller 4 from the roller groove part 21 and so on.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a rotary compressor used for, for example, a refrigerator-freezer or an air conditioner.

[0002]

2. Description of the Related Art Rotary compressors are widely used for refrigerators and air conditioners because of their compactness and simple structure. The compression mechanism such as vanes and rollers, which are main components of the compressor, is described in, for example, Kawahira, Hermetic Refrigerator (1993), page 14, FIG. 6.1.

The operation of a conventional rotary compressor will be described below with reference to FIG. A crankshaft 1 having an eccentric portion, a bearing for supporting the crankshaft 1, a cylinder 2, a vane 3, and a roller piston eccentrically rotating within the cylinder 2 (hereinafter referred to as a roller) in a closed container (not shown).
4, a vane 3 having an arc-shaped tip reciprocates in a groove 5 of the cylinder 2, and its tip is caused by a spring force of a spring 6 and a pressure difference between the inside and outside of the cylinder 2. The roller 2 is pressed against the outer peripheral surface of the roller 4 by the force, and slides in contact with the outer peripheral portion of the roller 4.
The interior is divided into a suction chamber 7 and a compression chamber 8. Generally, the bearing is composed of a main bearing 9 and an auxiliary bearing 10.

[0004] O is the center of the cylinder 2 and the crankshaft 1,
The crankshaft 1 has an eccentric portion (hereinafter, referred to as a crankpin) 11 centered on P, which is eccentric from the center O by e, and a roller 4 is fitted on the crankpin 11 and is driven by an electric motor (not shown). When the crankshaft 1 rotates and the roller 4 revolves in the cylinder 2, the refrigerant gas is sucked into the suction chamber 7, and the sucked refrigerant gas is compressed in the compression chamber 8 and discharged from a discharge port (not shown). Then, the discharged refrigerant is sent to the refrigeration cycle side, and is again sucked into the suction chamber 7 of the compressor via the condenser, the expansion valve, and the evaporator.

In the above configuration, the roller 4 and the vane 3
In the contact portion with the leading end, oil mainly contained in the suction refrigerant and oil passing through the gap between the vane 3 and the vane groove 5 provided in the cylinder 2 or the gap between the end faces of the roller 4 due to the pressure difference. An oil film had formed.

[0006]

However, in the above-described conventional configuration, the tip of the vane 3 has an arcuate curved surface,
Since the outer peripheral surface of the roller 4 is also a circular curved surface (cylindrical surface),
The contact state between the vane 3 and the roller 4 is equivalently a contact between the small cylinder and the large cylinder. Therefore, the contact state is a line contact state, the contact area is small, the load per unit area (contact stress) is large, and the contact sliding condition between the vane 3 and the roller 4 is severe.

The number of rotations of the roller 4 is also determined by the difference in sliding resistance between the inner peripheral surface of the roller 4 and the crankpin 11 and the sliding resistance between the outer peripheral surface of the roller 4 and the tip of the vane 3. The rotation speed of the roller 4 is very unstable (generally, when the rotation speed of the crankshaft 1 is operated at 3500 rpm, the rotation speed of the roller is about several tens to several hundreds rpm). For this reason, the sliding surface between the tip of the vane 3 and the roller 4 becomes an unstable sliding sliding in which the sliding speed changes depending on conditions and the oil film thickness also changes.

In particular, for the purpose of protecting the ozone layer, alternative refrigerants containing no chlorine (for example, R-134a) have been used. However, these refrigerants are more inferior in sliding state than the refrigerants containing chlorine. Therefore, there have been problems such as the need to severely restrict the use conditions of the compressor and to develop a sliding material with further improved wear resistance.

As one conventional example for solving this problem,
For example, in Japanese Patent Application Laid-Open No. 7-259767, as shown in FIG.
1, an oil groove 14 provided on the outer diameter of the crankpin 11 in communication with the horizontal hole 13, an outer groove 15 provided on the outer circumference of the roller 4, and an outer circumference thereof. A hole 16 passing through the groove 15 from the roller inner diameter, and an oil groove 17 provided in the deepest portion of the outer peripheral groove 15 in parallel with the outer peripheral groove 15.
Are disclosed. This is because the refrigerating machine oil pumped into the oil supply passage 12 inside the crankshaft is forcibly supplied between the roller and the vane by communicating the lateral hole 13 and the roller through hole 16 of the crankpin 11 to enclose the refrigerating machine oil. Even when the amount is small, an oil film is formed between the roller and the vane, and at the same time, the vane pressing force is reduced, increasing the reliability of the compressor and reducing the oil rate to improve the efficiency of air conditioners and the like. It is.

However, in this configuration, the sliding condition between the vane 3 and the roller 4 is improved as compared with the first conventional example, but the oil supply to the contact portion between the roller 4 and the vane 3 is relayed as described above. Since it has a complicated route with many points, processing is complicated, and there is a disadvantage that gas is easily accumulated and stable lubrication is difficult.

Further, the crankpin 11 and the inner peripheral surface of the roller 4 receive a very large force from the latter half of the compression process, but no consideration has been given to this.

The present invention solves the above-mentioned conventional problems, is easy to process, secures stable lubrication without adversely affecting other sliding parts, and reliably lubricates sliding parts between vanes and rollers. Accordingly, an object of the present invention is to provide a rotary compressor having higher reliability and a longer life.

[0013]

According to a first aspect of the present invention, there is provided a cylinder, a crankshaft having a crankpin, a bearing rotatably supporting the crankshaft, and a crankshaft driven by the crankpin. A roller piston that moves in the cylinder, a vane having a rounded or entire tip, and a vane tip that has substantially the same curvature as the vane tip and that the vane tip abuts, and is disposed on the outer peripheral surface of the roller piston. And a at least one flow path communicating from the groove to the light load side of the inner peripheral surface of the roller piston.

According to a second aspect of the present invention, there is provided the rotary compressor, wherein the flow path is provided so as to be inclined toward the suction chamber with respect to the reciprocating center axis of the vane.

According to a third aspect of the present invention, there is provided a cylinder, a crankshaft having a crankpin portion, and an oil formed around the crankshaft and the crankpin portion for sending refrigerating machine oil to each sliding portion. A groove, a bearing that rotatably supports the crankshaft, a roller piston that moves in the cylinder while being driven by the crankpin portion, a vane whose tip is entirely or partially rounded, and a vane tip of the vane. A groove disposed on the outer peripheral surface of the roller piston and having at least one flow path communicating from the groove to the inner peripheral surface of the roller piston. It is a rotary compressor.

According to a fourth aspect of the present invention, the flow path is provided in parallel with the reciprocating center axis of the vane, or inclined toward the suction chamber with respect to the reciprocating center axis of the vane. Rotary compressor.

According to a fifth aspect of the present invention, there is provided a cylinder, a crankshaft having a crankpin portion, a bearing rotatably supporting the crankshaft, and moving in the cylinder while being driven by the crankpin portion. A roller piston,
A vane having all or a part of the tip having an R shape, a groove disposed on the outer peripheral surface of the roller piston, having substantially the same curvature as the tip of the vane and contacting the tip of the vane;
A rotary compressor provided with an oil chamber formed by the roller piston, the bearing end face, the crank pin portion, and at least one flow path communicating from the groove portion to the oil chamber.

According to a sixth aspect of the present invention, there is provided a cylinder, a crankshaft having a crankpin portion, a bearing rotatably supporting the crankshaft, and moving in the cylinder while being driven by the crankpin portion. A roller piston,
A vane having all or a part of an end in an R shape, a groove disposed on the outer peripheral surface of the roller piston, having substantially the same curvature as the end of the vane, and contacting the end of the vane;
An oil chamber formed by the roller piston, the bearing end face, and the crank pin portion, and on one or both side surfaces of the roller piston so as to communicate from the groove portion to an oil chamber on an inner peripheral surface of the roller piston, Alternatively, the rotary compressor is provided with an oil supply passage having a width smaller than the thickness of the vane on one or both of the bearing end surfaces with which the side surfaces of the vane are in contact.

According to a seventh aspect of the present invention, there is provided a cylinder, a crankshaft having a crankpin portion, a bearing rotatably supporting the crankshaft, and moving in the cylinder while being driven by the crankpin portion. A roller piston,
A vane having all or a part of an end in an R shape, a groove disposed on the outer peripheral surface of the roller piston, having substantially the same curvature as the end of the vane, and contacting the end of the vane;
An oil supply flow having a width smaller than the thickness of the vane, provided on one or both side surfaces of the vane, or on one or both of the bearing end surfaces with which the side surfaces of the vane contacts, in a direction in which the vane reciprocates. And a rotary compressor having a path.

The present invention according to claim 8 is a cylinder, a crankshaft having a crankpin portion, a bearing rotatably supporting the crankshaft, and moving in the cylinder while being driven by the crankpin portion. A roller piston,
A vane having all or a part of an end in an R shape, a groove disposed on the outer peripheral surface of the roller piston, having substantially the same curvature as the end of the vane, and contacting the end of the vane;
A flow path communicating with the oil chamber from the bearing end face in contact with the side face of the vane, and provided on the side face of the vane or the bearing end face in contact with the vane so as to communicate with the flow path, having a width smaller than the thickness of the vane. This is a rotary compressor including an oil supply flow path.

According to a ninth aspect of the present invention, there is provided a rotary compressor in which a fine oil groove is provided in a part of a longitudinal direction or a whole length at a contact portion between the groove and the tip of the vane.

According to a tenth aspect of the present invention, in the contact portion between the groove and the tip of the vane, a part in the longitudinal direction within an angle smaller than an angle at which the tip of the vane swings in the groove. Or a rotary compressor having a plurality of fine oil grooves provided over the entire length.

[0023]

BEST MODE FOR CARRYING OUT THE INVENTION Hereinafter, an embodiment of a rotary compressor according to the present invention will be described.

The configuration of the rotary compressor according to one embodiment of the present invention is substantially the same as that of the conventional example described with reference to FIG. 8 except for a part such as a roller groove portion. The same reference numerals are given to the same components as those described in the above conventional example, and the description thereof will be omitted.

(Embodiment 1) Hereinafter, a first embodiment of the present invention will be described with reference to FIGS.

As shown in FIG. 1, an R-shaped roller groove 21 is provided in a part of the roller 4, and the tip of the vane 3 having substantially the same curvature is slidably disposed in the roller groove 21. The vane 3 is moved toward the inner peripheral surface of the roller 4.
A refueling hole 22 is provided on the light load side, which is inclined toward the suction chamber side of the reciprocating center axis, and is provided on the outer periphery of the crankshaft 1 and the crankpin 11 for sending refrigerating machine oil to each sliding portion. The oil groove 23 is formed. With this configuration, the rotation of the crankshaft 1 causes the roller 4 to revolve (eccentrically oscillate) in the cylinder 2 as the crankpin 11 moves, and the refrigerating machine oil uses centrifugal force and viscosity. Due to the pumping force, the oil flows through the oil groove 23 and is supplied to each sliding portion. A part of the oil is supplied to the leading end of the vane 3 and the sliding surface of the roller groove 21 through the oil supply hole 22. As described above, oil is supplied to the leading end of the vane 3 and the sliding surface of the roller groove portion 21 in the oil groove 2 where the high-pressure refrigerator oil always flows.
From 3, the path becomes a very simple path passing through the oil supply hole 22, and the gas hardly accumulates and the processing is simple.

FIG. 2 is a calculation example showing the relation between the magnitude of the force F applied to the inner peripheral surface of the roller 4 and the direction β in which the force F works with respect to the rotation angle θ of the crankshaft 1 and is shown in FIG. As described above, the force F applied to the inner peripheral surface of the roller 4 increases in accordance with the compression of the refrigerant gas, but the direction β of the force F is slightly different depending on the load and the specification, but in the fourth quadrant ( The rotation angle θ of the crankshaft 1 often ranges from 270 degrees to 360 degrees). For this reason, if the oil supply hole 22 is open in the high-load portion on the inner periphery of the roller 4, the oil film pressure generated on the inner peripheral surface of the roller 4 decreases, and the lubrication state of the inner periphery of the roller 4 deteriorates. . Therefore, if the angle α between the center of the hole 22 and the central axis of the reciprocating motion of the vane is α ≧ 0 for safety, the light load side of the inner peripheral surface of the roller 4 (in this calculation example, the force F is Refrigeration oil (lubricating oil) is supplied from about 1/3 of the peak), the lubrication state of the sliding surface of the tip of the vane 3 and the roller groove 21 is improved, and the lubrication state of the inner peripheral surface of the roller 4 is improved. There is no loss.

In this embodiment, two holes 22 are provided. However, the number of holes 22 may be determined according to the length of the roller groove 21 in the longitudinal direction or the like. Is not limited to a circle but may be a long hole or the like.

Further, in order to make it easy for the lubricating oil to spread to the sliding portion and to remove foreign matters, the roller groove 21 or the tip of the vane 3 in the longitudinal direction is partially or entirely provided that the lubrication oil is not adversely affected. Of course, a narrow groove may be provided.

Further, when the load on the inner peripheral surface of the roller is light (the load per unit area is small), such as in a system with a high pressure or a large diameter of the crank pin portion, α is negative (numerical value). Of course, it can be used in some cases.

(Embodiment 2) Hereinafter, a second embodiment of the present invention will be described with reference to FIG.

In FIG. 3, the inner peripheral surface of the roller 4 and the main bearing 9
An oil chamber 25 formed by the crank pin 11;
Oil supply hole 2 communicating with roller groove 21 and sliding portion of vane 3
6, an inner peripheral surface of the roller 4, an end surface of the auxiliary bearing 10, an oil chamber 27 formed by the crank pin 11, and an oil supply hole 28 communicating with the roller groove 21 and the sliding portion of the vane 3. It has a configuration. The refrigerating machine oil is always supplied (flowed) to the oil chambers 25 and 27, and the oil is supplied to the oil supply holes 26, 2, and 27.
8, the oil is supplied to the sliding portion between the roller groove 21 and the vane 3.

As described above, similarly to the first embodiment, the vane 3
The oil is supplied to the oil chamber 2 and the sliding surface of the roller groove 21 by the oil chamber 2.
It is a very simple route from 5, 27 through the oil supply holes 26, 28, it is difficult for gas to accumulate, and the processing is simple. In FIG. 3, two channels are shown as an example, but only one channel may be used. Of course it is.

(Embodiment 3) Hereinafter, a third embodiment of the present invention will be described with reference to FIG.

As shown in FIG. 4, the oil chamber 2 formed by the inner peripheral surface of the roller 4, the end surface of the sub bearing 10, and the crank pin 11
7, a flow path 29 communicating with the sliding portion between the roller groove 21 and the vane 3 is provided on the side surface of the roller 4, and a fine oil groove 30 is provided in the longitudinal direction of the roller groove 21. Oil chamber 27
Is always supplied (flowed) with the refrigerating machine oil, and the oil is supplied to the sliding portion between the roller groove portion 21 and the vane 3 through the flow path 29 to perform stable lubrication.

In FIG. 4, the flow path (oil supply flow path) 2
Although the case where there is one 9 has been described, the present invention is not limited to this, and for example, it may be provided on both side surfaces of the roller 4. Further, in FIG. 4, the case where the flow path 29 is provided on the side surface of the roller has been described. However, the present invention is not limited to this.

Embodiment 4 Hereinafter, a fourth embodiment of the present invention will be described with reference to the drawings.

As shown in FIG. 5, an oil supply passage 31 having a width smaller than the thickness of the vane 3 is provided on the side surface of the vane 3 in the longitudinal direction in which the vane 3 reciprocates. Refrigeration oil 32 in a closed container (not shown) from the side,
Due to the pressure difference, the oil is supplied to the leading end of the vane 3 and the sliding portion of the roller groove 21 through the flow path 31 and the fine oil groove 33 provided in the longitudinal direction of the roller groove 21 to perform stable lubrication. .

In FIG. 5, the case where the number of the flow passages 31 is one has been described.
May be provided on both sides. FIG. 5 illustrates the case where the flow path 31 is provided on the side surface of the vane 3. However, the present invention is not limited to this.
Needless to say, it may be provided on the end face side of 0.

(Embodiment 5) Hereinafter, a fifth embodiment of the present invention will be described with reference to the drawings.

As shown in FIG. 6, an oil supply hole 34 communicating with the refrigerating machine oil 32 in a closed container (not shown), and a vane 3 reciprocatingly moving along the center line of the vane 3 so as to communicate with the hole 34. The passage 35 having a width smaller than the thickness a of the sub bearing 10 is provided on the end face of the sub bearing 10 in contact with the vane 3. Here, the flow path of the present invention described in claim 8 corresponds to the oil supply hole 34, and the oil supply flow path of the present invention corresponds to the flow path 35.

The refrigerating machine oil 32 in the closed container from the lower end side of the vane 3 passes through the oil supply hole 34, the flow path 35, and the fine oil groove 36 provided in the longitudinal direction of the roller groove 21 due to the pressure difference. It is carried to the tip of the vane 3 and the sliding portion of the roller groove 21 to perform stable lubrication.

Although FIG. 6 illustrates the case where the flow path 35 is provided on the end face side of the bearing 10 in contact with the side surface of the vane 3, the present invention is not limited to this, and may be provided on the side surface of the vane 3. Of course it is.

Embodiment 6 Hereinafter, a sixth embodiment of the present invention will be described with reference to the drawings.

As shown in FIG. 7, the angle between the tip of the vane 3 and the roller groove 21 is slightly smaller than the angle 2δ at which the tip of the vane 3 swings in the roller groove 21 (both swing angle). A small oil groove 3 over a part of the longitudinal direction or over the entire length
7 and 38 are provided. With such a configuration, since the oil groove is present within the swing angle, the oil film can be stably held on the sliding portion that is the contact portion between the tip of the vane 3 and the roller groove 21.

In FIG. 7, the number of the grooves is two. However, more narrow grooves may be provided in portions which are considered to be in contact with each other. It is a matter of course that a road may be provided.

As described above, according to the first to sixth embodiments, the working is easy, and the other sliding parts are not adversely affected.
A stable lubrication is ensured at the abutting portion between the vane and the roller to ensure the lubrication of the sliding portion, and a more reliable and longer life rotary compressor can be realized.

[0048]

As is apparent from the above description, the present invention has an advantage that the lubrication of the sliding portion between the vane and the roller can be performed more stably than before.

[Brief description of the drawings]

FIG. 1 is a partial sectional view showing a configuration of a mechanical part of a rotary compressor according to a first embodiment of the present invention.

FIG. 2 is a graph showing the relationship between the magnitude of the force F applied to the inner peripheral surface of the roller and the direction β in which the force F acts on the rotation angle θ of the crankshaft in the rotary compressor of the present invention.

FIG. 3 is a partial sectional view showing a configuration of a mechanical part of a rotary compressor according to a second embodiment of the present invention.

FIG. 4 is a partial sectional view showing a configuration of a mechanical part of a rotary compressor according to a third embodiment of the present invention.

FIG. 5 is a partial sectional view showing a configuration of a mechanical part of a rotary compressor according to a fourth embodiment of the present invention.

FIG. 6 is a partial sectional view showing a configuration of a mechanical part of a rotary compressor according to a fifth embodiment of the present invention.

FIG. 7 is a sectional view of a main part showing a configuration of a rotary compressor according to a sixth embodiment of the present invention.

FIG. 8 is a partial cross-sectional view showing a configuration of a mechanical part of a conventional rotary compressor.

FIG. 9 is a partial cross-sectional view showing a configuration of a mechanical part of another conventional rotary compressor.

[Explanation of symbols]

 DESCRIPTION OF SYMBOLS 1 Crankshaft 2 Cylinder 3 Vane 4 Roller 9 Main bearing 10 Secondary bearing 11 Crank pin part 21 Roller groove part 22, 26, 28, 34 Oil supply hole 23 Oil groove 25, 27 Oil chamber 29, 31, 35 Flow path 30, 33, 36, 37, 38 Fine oil groove

Continued on the front page (72) Inventor Fumitoshi Nishiwaki 1006 Kadoma, Kadoma, Osaka Prefecture Inside Matsushita Electric Industrial Co., Ltd. Person Hiroshi Hasegawa 1006 Kazuma Kadoma, Kadoma City, Osaka Prefecture Inside Matsushita Electric Industrial Co., Ltd.

Claims (10)

[Claims] 1. A cylinder, a crankshaft having a crankpin part, a bearing rotatably supporting the crankshaft, a roller piston moving in the cylinder while being driven by the crankpin part, Or a vane part of which is R-shaped, a groove portion disposed on the outer peripheral surface of the roller piston, having substantially the same curvature as the vane tip, and contacting the vane tip, and an inner periphery of the roller piston from the groove portion. At least one or more flow paths communicating with a light load side of the surface. 2. The rotary compressor according to claim 1, wherein the flow path is provided so as to be inclined toward the suction chamber with respect to a reciprocating center axis of the vane. 3. A cylinder, a crankshaft having a crankpin portion, and a crankshaft formed on the outer periphery of the crankshaft and the crankpin portion.
An oil groove for sending refrigerating machine oil to each sliding portion; a bearing rotatably supporting the crankshaft; a roller piston moving in the cylinder while being driven by the crankpin portion; A portion having an R-shaped portion, a groove having substantially the same curvature as the tip of the vane, and having a contact with the tip of the vane, a groove disposed on the outer peripheral surface of the roller piston, and an inner peripheral surface of the roller piston from the groove. A rotary compressor provided with at least one or more flow paths communicating with each other. 4. The flow path is provided in parallel with the reciprocating central axis of the vane or inclined to the suction chamber side with respect to the reciprocating central axis of the vane. 4. The rotary compressor according to 3. 5. A cylinder, a crankshaft having a crankpin part, a bearing rotatably supporting the crankshaft, a roller piston moving in the cylinder while being driven by the crankpin part, Or a vane part of which is R-shaped, a groove portion disposed on the outer peripheral surface of the roller piston, having substantially the same curvature as the vane tip, and contacting the vane tip, the roller piston, the bearing end face, A rotary compressor, comprising: an oil chamber formed by a crankpin portion; and at least one or more flow paths communicating from the groove portion to the oil chamber. 6. A cylinder, a crankshaft having a crankpin portion, a bearing rotatably supporting the crankshaft, a roller piston moving in the cylinder while being driven by the crankpin portion, and Or a vane part of which is R-shaped, a groove portion disposed on the outer peripheral surface of the roller piston, having substantially the same curvature as the vane tip, and contacting the vane tip, the roller piston, the bearing end face, An oil chamber formed by a crank pin portion, and a bearing in which one or both side surfaces of the roller piston or a side surface of the vane is in contact with the oil chamber on the inner peripheral surface of the roller piston from the groove portion. A rotary compressor characterized in that an oil supply passage having a width smaller than the thickness of the vane is provided on one or both end faces. 7. A cylinder, a crankshaft having a crankpin portion, a bearing rotatably supporting the crankshaft, a roller piston moving in the cylinder while being driven by the crankpin portion, Or a vane part of which is R-shaped, a groove portion disposed on the outer peripheral surface of the roller piston, having substantially the same curvature as the vane tip, and contacting the vane tip, and one or both side faces of the vane Alternatively, an oil supply flow path having a width smaller than the thickness of the vane is provided on one or both of the bearing end surfaces with which the side surfaces of the vane are in contact, and provided in a direction in which the vane reciprocates. Rotary compressor. 8. A cylinder, a crankshaft having a crankpin portion, a bearing rotatably supporting the crankshaft, a roller piston moving in the cylinder while being driven by the crankpin portion, and Or a vane part of which has an R shape, a groove portion disposed on the outer peripheral surface of the roller piston, having substantially the same curvature as the vane tip, and contacting the vane tip, and a bearing end face contacting the side surface of the vane. A flow path communicating with the oil chamber; and an oil supply flow path having a width smaller than the thickness of the vane, provided on a side surface of the vane or a bearing end face in contact with the vane so as to communicate with the flow path. A rotary compressor, characterized in that: 9. A thin oil groove is provided in a portion in the longitudinal direction or over the entire length at a contact portion between the groove and the tip of the vane. 3. The rotary compressor according to claim 1. 10. A part of a longitudinal direction or a plurality of parts in a longitudinal direction within an angle smaller than an angle at which the vane tip swings in the groove, in a contact portion between the groove and the vane tip. The rotary compressor according to any one of claims 1 to 8, comprising a plurality of fine oil grooves.