JPH09209952A - Rotary compressor - Google Patents

Abstract

PROBLEM TO BE SOLVED: To improve compression performance and reliability in the case where a fleon substitute is used by providing a number of processing flaws in an outer circumferential surface of a roller which slides in contact with a tip surface of a vane. SOLUTION: A number of linear flaws 11a having inclination in a slide direction of a rotor 11 and crossing each other are provided as processing flaws in an outer circumferential surface of the roller 11 which slides in contact with a tip surface of a vane 12. Depth of the linear flaws 11a is favorably set to be about 0.8-1.0μm. The linear flaws 11a invade into a cylinder 4 to form an oil sump of lubricating oil. When the roller 11 passes a tip part of the vane 12, because the linear flaws 11a are inclined in a rotation direction of the roller 11, a contact part of lubricating oil in the linear flaws 11a with the vane 12 is moved as the roller 11 rotates, thereby the vane 12 is lubricated along the whole length of it. Friction abrasion between the roller 11 and the vane 12 can thus be reduced, thereby compression performance can be improved.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a rotary compressor.

[0002]

2. Description of the Related Art A conventional rotary compressor will be described with reference to FIGS.

An electric motor having a stator 2 and a rotor 3 and a compression element driven by the electric motor are housed in a closed container 1. In the compression element, a roller 11, which is rotatably fitted to an eccentric portion 10 of a crankshaft 9, rotates eccentrically in the cylinder 4 by the rotation of the crankshaft 9. Then, the inside of the cylinder 4 is partitioned by the vanes 12 pressed by the rollers 11, and the working fluid (refrigerant gas) sucked from the suction pipe 15 is compressed. The compressed gas is discharged into the closed container and discharged from the discharge pipe 19 to an external refrigeration cycle.

In the rotary compressor having such a structure, the most important issue in terms of reliability is the tribology between the roller 11, the vane 12 and the cylinder 4.
Usually, the roller 11, the vane 12, and the cylinder 4 are used in combination of metal materials, and there is a problem that abnormal lubrication occurs and compression performance is deteriorated in the case of poor lubrication.

In order to solve this problem, Japanese Patent Laid-Open No. 6-2
Japanese Laid-Open Patent Publication No. 57576 discloses that a slant groove having a depth of about 2 to 10 μm for retaining lubricating oil is provided on a surface of a roller of a compressor and a side wall surface of a vane to reduce wear of a contact sliding portion. .

[0006]

In the above rotary compressor of the prior art, since the contact portion between the roller and the vane is a linear contact, the surface pressure is very high and the temperature and pressure are high. Further, in the rotation speed control type compressor using an inverter, the compressor is operated in a rotation range from low speed to high speed in order to provide comfortable air conditioning by widening the range, low noise / vibration, and energy saving. In this case, in particular, in each sliding portion in the low speed rotation region, the operation is performed in the boundary lubrication region where it is difficult to form an oil film, and abnormal wear is likely to occur.

Further, the lubrication of the contact portion between the roller and the vane and the cylinder is carried out by the oil leaking into the cylinder through the clearance of the sliding portion of the roller and the vane, and the sliding portion of the roller and the vane. When the clearance is increased to increase the amount of lubricating oil supplied into the cylinder, there is a problem that heating loss due to oil increases and the performance of the compressor deteriorates.

Furthermore, CFC12, HFC which has been conventionally used as a working fluid for freezers / refrigerators and air conditioners.
Since CFC22 has chlorine in its molecule, it has been pointed out that it destroys the ozone layer in the stratosphere, which has become a social problem. Therefore, it is necessary to switch to CFC alternatives that do not cause ozone layer depletion, and HFC refrigerants that do not have chlorine in their molecules are the most promising candidates for these CFC alternatives. With this alternative Freon, unlike the previous Freon,
Since it is not possible to expect the lubricating action of chlorine as an extreme pressure agent, the lubrication condition becomes more severe, and there is a problem that the performance of the compressor deteriorates due to abnormal wear of the rollers and vanes.

The compressor described in Japanese Patent Laid-Open No. 6-257576 has a roller surface and a side wall surface of a vane provided with an oblique groove having a depth of about 2 to 10 μm for retaining lubricating oil. Since the depth of the groove is about 2 to 10 μm, there is a concern that a large amount of lubricating oil may enter into the cylinder from the oblique groove provided on the surface of the roller or the side wall surface of the vane, and the compression performance may be deteriorated.

The object of the present invention is to solve the problem of tribology at the contact portion between the roller, the vane and the cylinder even in the environment where the lubrication condition is severe, even when the alternative CFC which cannot be expected to have its own lubricating effect is used. It is to provide a rotary compressor having high compression performance and high reliability.

[0011]

The above object is to rotatably fit an electric motor having a stator and a rotor, a crankshaft driven by the electric motor, and an eccentric portion of the crankshaft in a closed container. A roller, a vane that reciprocates with its tip in contact with the roller to partition the inside of the cylinder into a low pressure suction chamber and a high pressure compression chamber, an end plate that supports the crankshaft, and closes both end openings of the cylinder. In a rotary compressor containing a compression element formed of a bearing and a sub-bearing, it is achieved by providing a large number of processing marks on the outer peripheral surface of the roller that is in sliding contact with the tip surface of the vane.

Further, it can be achieved by providing a large number of processing marks on the end surface of the roller that is in sliding contact with the end plates that close the openings at both ends of the cylinder.

Further, it can be achieved by providing a large number of processing marks on the inner peripheral surface of the roller which is in sliding contact with the eccentric portion of the crankshaft.

Further, the outer peripheral surface of the roller which is in sliding contact with the tip surface of the vane, the end surface of the roller which is in sliding contact with the end plates closing both end openings of the cylinder, and the roller which is in sliding contact with the eccentric portion of the crankshaft. This is achieved by simultaneously providing a large number of processing marks on the inner peripheral surface of the.

Further, it is achieved by providing a large number of processing marks on the tip end surface of the vane which is in sliding contact with the outer peripheral surface of the roller.

Further, it can be achieved by providing a large number of processing marks on the side wall surface of the vane which is in sliding contact with the vane groove of the cylinder.

It is provided.

Further, it can be achieved by providing a large number of processing marks on the end surface of the vane that is in sliding contact with the end plates that close the openings at both ends of the cylinder.

The tip surface of the vane slidingly contacting the outer peripheral surface of the roller, the side wall surface of the vane slidingly contacting the vane groove of the cylinder, and the vane slidingly contacting the end plates closing both end openings of the cylinder. This is achieved by simultaneously providing a large number of processing marks on the end face of the.

Here, the processing mark means that the depth of the processing mark is 0.
It is about 8 to 1.0 μm.

[0021]

DESCRIPTION OF THE PREFERRED EMBODIMENTS Embodiments of the present invention will be described below with reference to the drawings.

FIG. 8 is a vertical cross-sectional view of a part of a horizontal rotary compressor embodying the present invention, and FIG. 9 is a horizontal cross-sectional view corresponding to the CC cross section of FIG. 8 and 9, the closed container 1
Stores an electric motor including the stator 2 and the rotor 3, and a compression element driven by the electric motor. The cylinder 4 has a main bearing 5 and a sub bearing 6 that close the openings at both ends of the cylinder 4 to form a working chamber including a suction chamber 7 and a compression chamber 8. The crankshaft 9 has an eccentric portion 10, and the eccentric portion 10
The roller 11 is rotatably fitted to the roller. Vane 12
Is pressed against the roller 11 by the gas pressure (discharge pressure) in the closed container 1 and the spring 13, so that the cylinder 4
The inside is divided into a low-pressure suction chamber 7 and a high-pressure compression chamber 8.

In this structure, the compression operation of the rotary compressor is performed as follows. When the electric motor is energized,
The rotation of the rotor 3 drives the crankshaft 9, and the roller 11 fitted in the eccentric portion 10 makes eccentric rotational movement in the cylinder 4. By partitioning the inside of the cylinder 4 into the suction chamber 7 and the compression chamber 8 by the vane 12 pressed by the roller 11,
The working fluid (refrigerant gas) sucked into the suction chamber 7 through the suction pipe 15 is compressed, and the compressed gas is discharged through the discharge port 16.
a through the discharge valve 16 and the auxiliary bearing 6 and the discharge cover 17
Enters the discharge chamber 18 formed by the
It is discharged into the inside and discharged from the discharge pipe 19 to an external refrigeration cycle (not shown).

Oil supply to the bearing sliding portion is performed as follows. The rotation of the crankshaft 9 causes the vane 12 pressed by the roller 11 to reciprocate, changing the volume of the space on the back surface of the vane where the spring 13 is mounted. Due to the reciprocating pump action due to this volume change, the lubricating oil 14 stored in the bottom portion of the closed container 1 is sucked from the suction fluid diode 20, passed through the discharge fluid diode 21 and the oil supply pipe 22, and is formed on the crankshaft 9. The oil is supplied to the oil supply hole 23 and the oil supply groove 24 to lubricate the bearing sliding portion.

Next, the oil is supplied to the contact portion between the roller 11, the vane 12 and the cylinder by the leakage of the lubricating oil supplied to the bearing sliding portion from both end surfaces of the roller 11 into the cylinder 4.
Cylinder 4 for lubricating oil contained in the refrigerant in the refrigeration cycle
The amount of oil sucked in and the amount of lubricating oil on the back surface of the vane leaked into the cylinder 4 through the clearance between the cylinder 4 and the vane 12 are about several milliliters per minute. Further, not all of these lubricating oils contribute to the lubrication of the sliding surfaces of the roller 11 and the vane 12, but a very small amount actually contributes, and the rest becomes a mist in the cylinder 4 and enters the refrigeration cycle together with the refrigerant gas. Be exhaled. Conversely, cylinder 4
If a large amount of lubricating oil enters the inside, the compression performance will decrease.

From the above, the roller 11 and the vane 12 are
The contact area between the cylinder 4 and the cylinder 4 has a high surface pressure, and in a CFC alternative environment where a lubricating effect cannot be expected, how effective lubrication with a very small amount of lubricating oil is the greatest improvement in compression performance and reliability of the rotary compressor. It was a challenge.

The present invention was devised to solve the above problems, and the configuration, operation and effect will be described below.

An embodiment of the present invention will be described with reference to FIGS.

FIG. 1 is a perspective view showing the structure of the cylinder 4 portion of the rotary compressor of the present invention, in which a large number of processing marks are formed on the outer peripheral surface of the roller 11 which is in sliding contact with the tip surface of the vane 12.
A streak-like mark 11a is provided which intersects the vane 12 and the roller 11 with a slanting direction with an inclination. The depth of the streak 11a is preferably about 0.8 to 1.0 μm.

The streak-like mark 11a having such a structure serves as an oil pool of the lubricating oil that has entered the cylinder 4. When the roller 11 passes through the tip of the vane 12, the streak 11a is inclined with respect to the rotation direction of the roller 11, so that the contact point between the lubricating oil in the streak 11a and the vane 12 is the roller. With the rotation of 11, the vanes 1 move one by one
The contact portion at the tip of 2 will be lubricated over the entire length. That is, by providing the ridge-like marks 11a having an inclination with respect to the sliding direction of the vane 12 and the roller 11, the lubricating oil that has infiltrated can be continuously supplied to the sliding surface. As a result, frictional wear between the roller 11 and the vane 12 is reduced, and the compression performance can be improved.

When the streak mark 11a intersecting with an inclination is provided as in the present embodiment, the effect is greater than the streak mark having an inclination in one direction, but the streak mark in two directions is formed. Since it is provided, it takes time to process the stripe marks.

FIG. 2 (a) shows a large number of processing marks on the end face of the roller 11 which is in sliding contact with the main bearing 5 and the sub bearing 6 having the end plates for closing the openings of both ends of the cylinder 4, and the vane 12 and the roller 11 are formed. A line-like mark 11b is provided which intersects the sliding direction with an inclination. The depth of the streak 11b is preferably about 0.8 to 1.0 μm.

The streaky traces 11b serve as oil pools for the lubricating oil to improve the lubrication performance, so that the gap between the end plate that closes the openings at both ends of the cylinder 4 and the end surface of the roller 11 can be narrowed. As a result, the leakage of lubricating oil from the gap to the cylinder 4 is reduced, and the compression performance can be improved.

FIG. 2B shows an eccentric portion 10 of the crankshaft 9.
As a large number of processing marks on the inner peripheral surface of the roller 11 that is in sliding contact with
A line-like mark 11c is provided which intersects the vane 12 and the roller 11 in the sliding direction with an inclination. Streak marks 1
The depth of 1c is preferably about 0.8 to 1.0 μm.

This streak mark 11c becomes a reservoir of lubricating oil, and in order to reduce frictional wear of the contact portion between the eccentric portion 10 of the crankshaft 9 and the inner peripheral surface of the roller 11, the lubricating oil is supplied to the contact portion. The amount can be reduced as compared with the case without the streak mark 11c. As a result, it is possible to reduce the leakage amount of the bearing lubricating oil from both ends of the roller 11 into the cylinder 4, and it is possible to improve the compression performance.

FIG. 2C shows a large number of processing marks on the outer peripheral surface, the end surface and the inner peripheral surface of the roller 11, which are stripe-shaped marks intersecting the sliding direction of the vane 12 and the roller 11 with an inclination. 11a, 11b and 11c are provided at the same time. With this configuration, the effects shown in FIGS. 2A and 2B can be achieved at the same time.

FIG. 3 shows, in the sliding direction of the vane 12 and the roller 11, the streak-like marks intersecting with the sliding direction of the vane 12 and the roller 11 in FIGS. It is a line-shaped mark with an inclination in the direction.
The depth of this streak-like mark is preferably about 0.8 to 1.0 μm.

With this structure, it is possible to improve the compression performance with a smaller number of processing steps than the number of streak marks intersecting at an angle.

The effect of improving the compression performance is smaller than that of the streak-like marks intersecting with an inclination, but it is sufficiently effective as compared with the case where there is no processing mark.

FIG. 4 shows the streak mark in FIGS. 1 and 2 as a concave mark. The size of the concave mark is a dozen or more μ in diameter
m, the depth is preferably about 0.8 to 1.0 μm. The concave mark does not have to be circular and may have a size corresponding to a diameter of ten and several μm.

The concave mark having such a structure serves as an oil pool of the lubricating oil that has entered the cylinder 4. And the roller 11
When passing through the tip of the vane 12, the contact width between the roller 11 and the vane 12 is larger than the diameter of the concave mark of ten and several μm, so that the incompressible lubricating oil in the oil reservoir does not escape to the outside. A high-pressure oil film pressure is generated between the roller 11 and the vane 12 to form an oil film. Therefore, the roller 11
The vane 12 and the vane 12 are not in contact with each other, and direct metal contact is suppressed, so that frictional wear is reduced and compression performance can be improved.

Another embodiment of the present invention will be described with reference to FIG.

In FIG. 5A, a large number of processing marks are formed on the tip surface of the vane 12 which is in sliding contact with the outer peripheral surface of the roller 11 and intersect the sliding direction of the vane 12 and the roller 11 with an inclination. The streak mark 12a is provided. The depth of the streak 12a is preferably about 0.8 to 1.0 μm.

According to this embodiment, the lubricating oil that has penetrated into the cylinder 4 can be continuously replenished to the sliding surface, the frictional wear of the roller 11 and the vane 12 can be reduced, and the compression efficiency can be improved. it can.

In the case of the present embodiment, the area to be machined is smaller than that in the case of forming the crossed stripe marks on the rollers of FIGS. 1 and 2, so that the productivity can be improved.

In FIG. 5 (b), a large number of processing marks are formed on the side wall surface of the vane 12 which is in sliding contact with the vane groove of the cylinder 4 and intersect with the sliding direction of the vane 12 and the roller 11 with an inclination. The streak mark 12b is provided. The depth of the streak 12b is preferably about 0.8 to 1.0 μm.

The streak 12b having such a structure serves as an oil pool of the lubricating oil, and the vane groove of the cylinder 4 and the vane 12 are formed.
The frictional wear of the contact portion with the side wall surface of is reduced. For this reason,
It is possible to reduce the amount of lubricating oil supplied by narrowing the gap between the two. As a result, the amount of lubricating oil leaking from the back surface of the vane into the cylinder 4 can be reduced, and the compression performance can be improved.

FIG. 5 (c) shows the sliding of the vane 12 and the roller 11 as a large number of machining marks on the end surface of the vane that is in sliding contact with the main bearing 5 and the sub bearing 6 having the end plates that close the openings at both ends of the cylinder 4. It is provided with streak-like marks 12c that intersect with each other with an inclination with respect to the direction. The depth of the streak 12c is preferably about 0.8 to 1.0 μm.

Even in such a configuration, the same effect as that of FIG. 5B can be obtained.

FIG. 5 (d) is an implementation of all that shown in FIGS. 5 (a) to 5 (c), and all the effects of FIGS. 5 (a) to 5 (c) can be obtained. .

FIG. 6 shows the crossed streaky marks in FIG. 5 as streaky marks having an inclination in one direction.
The depth of this streak-like mark is preferably about 0.8 to 1.0 μm.

With this configuration, it is possible to improve the compression performance by reducing the frictional wear and the lubricating oil that penetrates into the cylinder 4 in a working process that is less than the streak mark that intersects with an inclination. it can.

The effect of reducing frictional wear and suppressing the intrusion of lubricating oil is smaller than that of the streak marks intersecting with an inclination, but it is sufficiently effective as compared with the case where there is no processing mark.

FIG. 7 shows the streak marks in FIGS. 5 and 6 as concave marks. The size of the concave mark is a dozen or more μm in diameter
The depth is preferably about 0.8 to 1.0 μm. The concave mark does not have to be circular and may have a size corresponding to a diameter of ten and several μm.

This concave mark becomes a reservoir of lubricating oil. Then, at the contact portion between the roller 11 and the vane 12,
The contact width between the roller 11 and the vane 12 is a diameter of a concave mark of a few dozen μ
Since it is larger than m, the incompressible lubricating oil in the oil reservoir has no escape to the outside and generates a high oil film pressure between the roller 11 and the vane 12 to form an oil film. Therefore, the roller 11 and the vane 12 are not in contact with each other, direct metal contact is suppressed, frictional wear is reduced, and compression performance can be improved.

Further, in the contact portion between the cylinder 4 and the vane 12, the contact surface is larger than the diameter of the recessed mark of ten and several μm, so that the incompressible lubricating oil in the oil reservoir escapes to the outside. There is no pressure, and a high oil film pressure is generated between the roller 11 and the vane 12 to form an oil film. Therefore, the cylinder 4 and the vane 12 are not in contact with each other. as a result,
Since the distance between the cylinder 4 and the vane 12 can be narrowed and the amount of lubricating oil leaking into the cylinder 4 can be reduced, the compression performance can be improved.

In each of the above embodiments, the roller 11
There is a machining mark on either the surface or the vane 12 surface,
It is possible to provide processing marks on both the roller 11 surface and the vane 12 surface.

However, on the surface where the roller 11 and the vane 12 are in contact with each other, it is more effective to provide a processing mark on either the roller 11 surface or the vane 12 surface.

The compressor of the present invention is most suitable for refrigeration, refrigerators and air conditioners for compressing alternative CFCs which are not expected to have a lubricating effect. However, even if the fluid to be compressed is other than CFCs, it is possible to improve the compression performance. You can

Further, in this embodiment, the rotary compressor having one cylinder in the cycle has been described as an example, but the present invention can be applied to a rotary compressor having two cylinders. Further, in addition to the compressor, the present invention is applicable to an expander and a vacuum pump having the same rotary type as the present invention.

Next, a method of processing a large number of processing marks on the outer peripheral surface, the end surface and the inner peripheral surface of the roller 11, the tip surface of the vane 12, the side wall surface and the end surface will be described.

The grinding method is most suitable for the processing of the streak marks of the present invention, and the final finished surface itself is sufficient. The manufacturing cost is also cheaper than others. Difficulties are that it is not possible to process concave marks and that burrs are easily generated during grinding.

The etching method is suitable for mass production because a large number of holes and grooves can be processed simultaneously and easily. But,
The biggest disadvantage is that the mask must be manufactured through processes such as film formation, exposure, development, and cleaning.

The laser beam processing method is used as a multipurpose processing method such as drilling, cutting and welding. Although it can be processed in the atmosphere and can be easily automated, it has problems in inner circumference processing and manufacturing costs.

Since the electron beam processing method has high processing accuracy, it is used for fine groove processing of rotary encoder disks. However, it is expensive because it is processed in a vacuum.

The ion beam processing method has very good processing accuracy, but it is processed in a vacuum like the electron beam,
The disadvantage is that a mask pattern has to be manufactured.

The electric discharge machining method is used for manufacturing fine nozzles and molds, has high machining accuracy and is inexpensive to manufacture. However, it is difficult to manufacture electrodes and is not suitable for mass production.

The plastic working method includes a rolling method called precision forging, shot blasting, sand blasting and bead blasting. It is superior to others in terms of processing speed and manufacturing cost. It is most suitable for processing the concave mark of the present invention.

[0069]

As described above, according to the present invention, the lubrication state between the roller, the vane, and the cylinder is significantly improved, and the leakage of the lubricating oil into the cylinder is reduced to improve the compression performance. Can be provided.

[Brief description of drawings]

FIG. 1 is a perspective view showing a configuration of a cylinder portion of a rotary compressor according to an embodiment of the present invention.

FIG. 2 is a perspective view of an embodiment of a roller with crossed ridge marks according to the present invention.

FIG. 3 is a perspective view of a roller provided with unidirectional stripe marks according to an embodiment of the present invention.

FIG. 4 is a view of a roller provided with a concave mark according to an embodiment of the present invention.
It is a perspective view of LA.

FIG. 5 is a perspective view of another embodiment of a vane having crossed streaks according to the present invention.

FIG. 6 is a perspective view of another embodiment of a vane having unidirectional stripe marks according to the present invention.

FIG. 7 is a perspective view of another embodiment of a vane having concave marks according to the present invention.

FIG. 8 is a sectional view showing a part of a rotary compressor embodying the present invention.

9 is a view as viewed in the direction of arrows CC in FIG. 8;

[Explanation of symbols]

11 ... Rollers, 11a to 11c ... Crossed streaky marks on the roller surface, 11d to 11f ... One-way streaky marks on the roller surface, 11g to 11i ... Concave marks on the roller surface, 12 ... Vane, 12a ~ 12c ... crossed streaky marks on the vane surface, 12d ~ 12f ... one-way streak marks on the vane surface,
12g to 12i ... A concave mark on the surface of the vane.

 ─────────────────────────────────────────────────── ─── Continuation of the front page (72) Inventor Masayoshi Koyama 502 Jinritsucho, Tsuchiura-shi, Ibaraki Hiritsu Manufacturing Co., Ltd.Mechanical Research Laboratory (72) Inventor Hirokatsu Kazogabe 502, Jinritsucho, Tsuchiura-shi, Ibaraki Hiritsu Co., Ltd. Machinery Research Laboratory (72) Inventor Hiroaki Hatake 800 Tomita, Ohira-cho, Shimotsuga-gun, Tochigi Prefecture Hitachi Co., Ltd.

Claims (16)

[Claims] 1. A cylinder, a roller fitted to a crank shaft in the cylinder, a vane fitted to the cylinder so that a tip end thereof is in sliding contact with the roller, a side surface of the roller and the vane. A rotary compressor having end plates disposed on both end surfaces of a cylinder so as to be in sliding contact with a side surface, wherein a machining mark is provided on a surface of the roller on which the vane slides. 2. A cylinder, a roller fitted to a crank shaft in the cylinder, a vane fitted to the cylinder such that a tip end thereof is in sliding contact with the roller, a side surface of the roller and the vane. A rotary compressor having end plates disposed on both end surfaces of a cylinder so as to be in sliding contact with a side surface, wherein a machining mark is provided on a surface of the roller that is in sliding contact with the end plates. 3. A cylinder, a roller fitted to a crank shaft in the cylinder, a vane fitted to the cylinder so that a tip end thereof is in sliding contact with the roller, a side surface of the roller and the vane. A rotary compressor having end plates arranged on both end surfaces of a cylinder so as to be in sliding contact with a side surface, wherein a machining mark is provided on the crankshaft fitting surface of the roller. 4. A cylinder, a roller fitted to a crank shaft in the cylinder, a vane fitted to the cylinder such that a tip end thereof is in sliding contact with the roller, a side surface of the roller and the vane. In a rotary compressor including end plates disposed on both end surfaces of a cylinder so as to be in sliding contact with a side surface, a surface of the roller in which the vane slides, a surface of the roller in sliding contact with the end plate, and the roller A rotary compressor characterized in that a machining mark is provided on each of the crankshaft fitting surfaces. 5. A cylinder, a roller fitted to a crank shaft in the cylinder, a vane fitted to the cylinder so that a tip end thereof is in sliding contact with the roller, a side surface of the roller and a vane of the vane. A rotary compressor having end plates disposed on both end surfaces of a cylinder so as to be in sliding contact with a side surface, wherein a working mark is provided on the roller sliding contact portion of the vane. 6. A cylinder, a roller fitted to a crank shaft in the cylinder, a vane fitted to the cylinder such that a tip end thereof is in sliding contact with the roller, a side surface of the roller and a vane of the vane. A rotary compressor having end plates disposed on both end surfaces of a cylinder so as to be in sliding contact with a side surface, wherein a machining mark is provided on the cylinder sliding contact surface of the vane. 7. A cylinder, a roller fitted to a crankshaft in the cylinder, a vane fitted to the cylinder so that a tip end thereof is in sliding contact with the roller, a side surface of the roller and the vane. A rotary compressor having end plates disposed on both end faces of a cylinder so as to be in sliding contact with a side surface, wherein a working mark is provided on the end plate sliding contact face of the vane. 8. A cylinder, a roller fitted to a crank shaft in the cylinder, a vane fitted to the cylinder so that a tip end thereof is in sliding contact with the roller, a side surface of the roller and a vane of the vane. A rotary compressor provided with end plates disposed on both end surfaces of a cylinder so as to be in sliding contact with a side surface, wherein the roller slide contact portion of the vane, the cylinder slide contact surface of the vane, and the end plate slide of the vane. A rotary compressor characterized by being provided with processing marks on each of the contact surfaces. 9. The rotary compressor according to claim 1, wherein the processing marks are parallel streaks. 10. The rotary compressor according to claim 1, wherein the processing mark has a concave shape. 11. A cylinder, a roller fitted to a crank shaft in the cylinder, a vane fitted to the cylinder such that a tip end thereof is in sliding contact with the roller, a side surface of the roller and the vane. In a roller processing method of a rotary compressor having end plates arranged on both end surfaces of a cylinder so as to be in sliding contact with a side surface, the roller has parallel streak marks formed by cutting at a desired position after final shaping. A roller processing method for a rotary compressor, comprising: 12. A cylinder, a roller fitted to a crank shaft in the cylinder, a vane fitted to the cylinder such that a tip end thereof is in sliding contact with the roller, a side surface of the roller and the vane. In a roller processing method for a rotary compressor including end plates arranged on both end surfaces of a cylinder so as to be in sliding contact with a side surface, the roller is provided with a concave mark by plastic working at a desired position after final shaping. A method for processing a roller of a rotary compressor, characterized by: 13. A cylinder, a roller fitted to a crank shaft in the cylinder, a vane fitted to the cylinder so that a tip end thereof is in sliding contact with the roller, a side surface of the roller and the vane. In a vane processing method for a rotary compressor having end plates disposed on both end surfaces of a cylinder so as to be in sliding contact with side surfaces, the vane is a linear stripe mark formed by cutting at a desired position after final shaping. A method for processing a vane of a rotary compressor, comprising: 14. A cylinder, a roller fitted to a crank shaft in the cylinder, a vane fitted to the cylinder so that a tip end thereof is in sliding contact with the roller, a side surface of the roller and the vane. In a vane processing method for a rotary compressor including end plates disposed on both end surfaces of a cylinder so as to be in sliding contact with a side surface, the vane is provided with a concave mark by plastic working at a desired position after final shaping. A method for processing a vane of a rotary compressor, characterized by: 15. A freezer / refrigerator using the rotary compressor according to any one of claims 1 to 10. 16. An air conditioner using the rotary compressor according to any one of claims 1 to 10.