JP5689151B2 - Rotary compressor - Google Patents

Description

  The present invention relates to a rotary compressor used in a refrigeration cycle or the like, and more particularly to a technique for improving the wear resistance of a vane of the rotary compressor.

  R12 and R22 have been mainly used as refrigerants for rotary compressors used in refrigeration cycles, etc., but these refrigerants R12 and R22 are released into the atmosphere and reach the ozone layer above the earth. Because of the problem of destroying the ozone layer, it is subject to Freon regulation. Then, although it moved to the refrigerant | coolant which does not contain this chlorine group, for example, a HFC refrigerant | coolant, there is still the subject of global warming and the natural refrigerant | coolant is examined.

  Of the sliding parts of the rotary compressor, the most severe sliding condition is the contact portion between the vane and the rolling piston.

  An HFC refrigerant (for example, R410A), which is one of the alternative refrigerants, does not include a chlorine atom in its molecule unlike R22, and therefore does not form an iron chloride film having excellent wear resistance at the sliding portion. Therefore, with the introduction of the HFC refrigerant, nitriding treatment or coating is performed on the vane in order to improve the wear resistance of the vane (see, for example, Patent Document 1).

  Furthermore, HFC refrigerants, particularly natural refrigerants, tend to have a higher wear resistance coating on the vanes because the compressor operating pressure is higher than before.

Japanese Patent No. 3666894 JP 2002-242867 A JP 2001-263280 A JP 2002-5063 A JP 11-236890 A

  A vane of a conventional rotary compressor has a relatively small vane tip radius, and the ratio of the vane tip radius to the vane thickness is about 1.10 to 1.90. When two elastic bodies of a vane and a rolling piston are pressed, they generally make surface contact instead of point or line contact, and Hertz stress is generated at the contact portion (Hertz elastic contact theory). As the ratio of the vane tip radius to the vane thickness decreases, the Hertz stress increases. Various coatings are applied to improve the abrasion resistance of the vane, but the coating may peel off when the Hertzian stress is high. Although the coating is rarely peeled off at an operating pressure comparable to that of an HFC refrigerant, there has been a problem that peeling of the coating is likely to occur under a carbon dioxide refrigerant where the operating pressure is high.

  The present invention has been made in order to solve the above-described problems. A rotary compressor provided with a vane having sufficient sliding resistance even in an application using a natural refrigerant such as carbon dioxide as a refrigerant. The purpose is to provide.

The rotary compressor according to the present invention is a rotary compressor that has a compression element and an electric element that drives the compression element in a sealed container, and uses carbon dioxide gas as a refrigerant.
The compression element includes a cylinder in which a groove is formed, a rolling piston that rotates eccentrically in the cylinder, and a vane that slidably contacts the rolling piston and reciprocates in the groove of the cylinder, and the rolling of the vane DLC-Si coating is applied to the surface that is in sliding contact with the piston, the cross section of the sliding contact portion that is in sliding contact with the rolling piston of the vane is formed in an arc shape, and the radius of the arc is at least twice the thickness of the vane It is.

  With the above-described configuration, the rotary compressor according to the present invention can provide a rotary compressor including a vane having sufficient sliding resistance even for an application using a natural refrigerant such as carbon dioxide as a refrigerant.

It is a figure which shows Embodiment 1, and is a longitudinal cross-sectional view of a rotary compressor. It is a figure which shows Embodiment 1, and is sectional drawing which shows the contact state of a vane and a rolling piston. It is a figure which shows Embodiment 1, and is a figure which shows the specification of the rotary compressor used for the durability test. It is a figure which shows Embodiment 1, and is a figure which shows the amount of wear in the Hertz stress when a ratio of the vane front-end | tip R with respect to a vane width | variety is changed, and a durability test. It is a figure which shows Embodiment 1, and is a figure which shows the abrasion loss in an endurance test.

Embodiment 1 FIG.
1 to 5 are diagrams showing Embodiment 1, FIG. 1 is a longitudinal sectional view of a rotary compressor, FIG. 2 is a sectional view showing a contact state between a vane and a rolling piston, and FIG. 3 is subjected to an endurance test. FIG. 4 is a diagram showing the specifications of the rotary compressor, FIG. 4 is a diagram showing the Hertz stress when the ratio of the vane tip R to the vane width is changed, and the wear amount in the durability test, and FIG. 5 is a diagram showing the wear amount in the durability test. It is.

  As shown in FIG. 1, the rotary compressor includes a compression element 10, an electric element 13, and a refrigeration (not shown) in a sealed container 4 including a body 1, an upper dish container 2, and a lower dish container 3. Contains machine oil. The compression element 10 includes an upper bearing 6, a lower bearing 7 that closes both ends of the cylinder 5 that forms a compression chamber therein, a rolling piston 9 that fits in an eccentric portion of the drive shaft 8, and a groove in the cylinder 5. The vane 14 etc. which reciprocate and the front-end | tip contacts the rolling piston 9 are comprised. The electric element 13 includes a stator 12 fixed to the body portion 1 and a rotor 11 that rotates inside the stator 12.

  As shown in FIG. 2, a compression chamber is formed by being surrounded by the vane 14, the rolling piston 9, the cylinder 5, and the upper bearing 6 and the lower bearing 7 that close the openings at both ends of the cylinder 5. When the drive shaft 8 rotates counterclockwise in FIG. 2, the rolling piston 9 rotates eccentrically in the cylinder 5, and the refrigerant gas sucked from the suction port 15 is compressed and discharged from the discharge port 16. In this suction-compression-discharge stroke, a pressing force is generated at the contact portion between the vane 14 and the rolling piston 9.

  The vane 14 is pressed against the rolling piston 9 by the pressure difference between the vane spring and the cylinder 5 inside and outside. In the rotary compressor, when the vane 14 reciprocates along the groove of the cylinder 5 in accordance with the eccentric rotational movement of the rolling piston 9, the tip of the vane 14 has the spring force of the vane spring and the inside and outside of the cylinder 5. In the state of being biased by the pressure difference, the sliding with the outer peripheral surface of the rolling piston 9 causes wear on the tip of the vane 14 and the outer peripheral surface of the rolling piston 9.

  Further, since the side surface of the vane 14 slides in contact with the groove of the cylinder 5 and the sliding surfaces of the upper bearing 6 and the lower bearing 7, the side surface of the vane 14 is also worn. Furthermore, since the drive shaft 8 slides with the bearing portions of the upper bearing 6 and the lower bearing 7 that support the rotation of the drive shaft 8, the drive shaft 8 and the bearing portion are worn.

  Therefore, in order to reduce the wear of each sliding portion, refrigeration oil is stored in the sealed container 4, and refrigeration oil (not shown) is supplied to each sliding portion to lubricate each sliding portion. And reduce wear.

  An example of the coated vane 14 will be described. In the vane 14, the sliding contact portion with the rolling piston 9 is formed in the same arc shape in cross section in the longitudinal direction. In order to improve the wear resistance of the vanes 14, a coating is applied. A base material (material is high-speed tool steel: SKH51 (JIS)) is subjected to nitriding treatment to form a nitrided diffusion layer, and further a DLC-Si (diamond-like carbon-silicon) coating layer is formed thereon. The DLC-Si coating layer is amorphous carbon containing silicon. The coating needs to be applied at least to the sliding contact portion with the rolling piston 9. If the coating is applied to the whole, the wear resistance of the sliding contact portion with the cylinder 5, the upper bearing 6, and the lower bearing 7 is also improved.

  In addition to the DLC-Si coating, there are coatings such as CrN (chromium nitride), TiN (titanium nitride), and DLC (diamond-like carbon). The CrN coating has good film adhesion strength, film wear and sliding properties. The same applies to the TiN coating. Furthermore, the DLC coating has good film abrasion, slidability, and attack on the mating material.

  In the present embodiment, attention has been paid to the fact that the Hertz stress already described is reduced when the tip R of the vane 14 is increased. When the vane 14 is not coated, the tip R of the vane 14 is designed to be relatively small so that the wear of the vane 14 proceeds and the corners of the vane 14 do not slide on the rolling piston 9. When coating the vane 14, it can be expected that the vane 14 will not wear. Therefore, it is conceivable that the tip R of the vane 14 is designed to be large from the beginning so that the Hertzian stress is reduced to suppress the peeling of the coating. .

  Therefore, as shown in FIG. 3, three types of rotary compressors for durability tests with different tips R of the vanes 14 were manufactured. The vane 14 has a width (thickness) of 3.2 mm, an outer diameter of the rolling piston 9 of 34 mm, and an eccentric amount of the drive shaft 8 of 3 mm, which are the same for all three types of rotary compressors. In addition, the vanes 14 of all three rotary compressors were coated. And the thing whose tip R radius of vane 14 is 9 mm, 6.7 mm, and 5.4 mm was prepared. These ratios of the vane tip radius to the vane width are 2.8, 2.1, and 1.7, respectively.

  The test conditions for the durability test were determined assuming use under a carbon dioxide refrigerant. The results of the durability test are shown in FIGS. For reference, data for a rotary compressor that does not coat the vanes 14 is also shown. As shown in FIG. 4, when the ratio of the tip R to the vane width is reduced, the Hertz stress tends to increase. In a rotary compressor that does not coat the vane 14, the amount of wear increases as the ratio of the tip R to the vane width decreases.

  Now, as shown in FIG. 4, the rotary compressors of the specifications A, B and C in FIG. 3 do not wear because the coatings of the specifications A and B are not peeled off. The specification C shows that the Hertz stress increases, so that the coating peels off during the durability test, and then wear progresses.

  FIG. 5 shows the change in the amount of wear with time, but the ratio of the vane tip R radius to the vane width is 2.8 and the coating is not worn. When there is no coating, the amount of wear increases with the passage of time when the ratio of the vane tip radius to the vane width is 2.8 and 1.25.

  As described above, the ratio of the vane tip R radius to the vane width is 2 or more. When the ratio of the vane tip radius to the vane width is 2 or less, the Hertzian stress increases, so that the coating peels off and wears.

  Coatings include DLC-Si, CrN, TiN, DLC, etc. However, as a result of the above durability test, it is understood that peeling does not occur in any coating as long as the ratio of the vane tip R radius to the vane width is 2 or more. It was.

  Needless to say, with a refrigerant other than carbon dioxide, if the ratio of the vane tip R radius to the vane width of the coated vane 14 is 2 or more, the coating cannot be removed.

  1 body part, 2 upper dish container, 3 lower dish container, 4 closed container, 5 cylinder, 6 upper bearing, 7 lower bearing, 8 drive shaft, 9 rolling piston, 10 compression element, 11 rotor, 12 stator, 13 electric element , 14 vanes, 15 inlets, 16 outlets.

Claims (2)

In a rotary compressor that has a compression element and an electric element that drives the compression element in a sealed container and uses carbon dioxide gas as a refrigerant.
The compression element includes a cylinder in which a groove is formed, a rolling piston that rotates eccentrically in the cylinder, and a vane that slidably contacts the rolling piston and reciprocates in the groove of the cylinder, and the rolling of the vane DLC-Si coating is applied to the surface that is in sliding contact with the piston, the cross section of the sliding contact portion that is in sliding contact with the rolling piston of the vane is formed in an arc shape, and the radius of the arc is at least twice the thickness of the vane And
The vane is formed by nitriding a base material of SKH51 to form a nitrided diffusion layer, and applying the DLC-Si coating on the nitrided diffusion layer to form a DLC-Si coating layer. A rotary compressor characterized by being.   The rotary compressor according to claim 1, wherein the radius of the arc is about 2.8 times the thickness of the vane.

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