CN1928362A - Refrigerant compressor, cooling system and refrigerator - Google Patents

Refrigerant compressor, cooling system and refrigerator Download PDF

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Publication number
CN1928362A
CN1928362A CNA2006101516342A CN200610151634A CN1928362A CN 1928362 A CN1928362 A CN 1928362A CN A2006101516342 A CNA2006101516342 A CN A2006101516342A CN 200610151634 A CN200610151634 A CN 200610151634A CN 1928362 A CN1928362 A CN 1928362A
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CN
China
Prior art keywords
molybdenum disulfide
piston
sliding
refrigerant compressor
mixed layer
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Pending
Application number
CNA2006101516342A
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Chinese (zh)
Inventor
岩田博光
片山诚
梅冈郁友
吉见祐基
川端淳太
石田贵规
石渡正人
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Fuji Manufacturing Co Ltd
Panasonic Holdings Corp
Original Assignee
Fuji Manufacturing Co Ltd
Matsushita Electric Industrial Co Ltd
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Filing date
Publication date
Application filed by Fuji Manufacturing Co Ltd, Matsushita Electric Industrial Co Ltd filed Critical Fuji Manufacturing Co Ltd
Publication of CN1928362A publication Critical patent/CN1928362A/en
Pending legal-status Critical Current

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/02—Lubrication
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/02—Lubrication
    • F04B39/0223—Lubrication characterised by the compressor type
    • F04B39/023—Hermetic compressors
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/0005—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00 adaptations of pistons
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/12—Casings; Cylinders; Cylinder heads; Fluid connections
    • F04B39/126—Cylinder liners
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/30—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
    • F04C18/34—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members
    • F04C18/356—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the outer member
    • F04C18/3562—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the outer member the inner and outer member being in contact along one line or continuous surfaces substantially parallel to the axis of rotation
    • F04C18/3564—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the outer member the inner and outer member being in contact along one line or continuous surfaces substantially parallel to the axis of rotation the surfaces of the inner and outer member, forming the working space, being surfaces of revolution
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C23/00—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids
    • F04C23/008—Hermetic pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05C—INDEXING SCHEME RELATING TO MATERIALS, MATERIAL PROPERTIES OR MATERIAL CHARACTERISTICS FOR MACHINES, ENGINES OR PUMPS OTHER THAN NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES
    • F05C2203/00—Non-metallic inorganic materials
    • F05C2203/08—Ceramics; Oxides
    • F05C2203/0804—Non-oxide ceramics
    • F05C2203/0856—Sulfides
    • F05C2203/086—Sulfides of molybdenum
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05C—INDEXING SCHEME RELATING TO MATERIALS, MATERIAL PROPERTIES OR MATERIAL CHARACTERISTICS FOR MACHINES, ENGINES OR PUMPS OTHER THAN NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES
    • F05C2253/00—Other material characteristics; Treatment of material
    • F05C2253/12—Coating

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Compressor (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
  • Sliding-Contact Bearings (AREA)
  • Shafts, Cranks, Connecting Bars, And Related Bearings (AREA)

Abstract

A refrigerant compressor having a compression element comprising sliding components made of metallic materials, wherein a mixed layer is formed by solid-dissolving molybdenum disulfide in at least one of the sliding faces of the sliding components, and a single molybdenum disulfide layer is further formed on the surface of the mixed layer. With this configuration, initial break-in is done using the single layer, and sliding loss is reduced. Even if the single layer peels off, because the molybdenum disulfide of the mixed layer is cleaved at a low friction coefficient, solid lubrication action is attained, the friction coefficient of the sliding section is lowered, and sliding loss is reduced.

Description

Refrigerant compressor, cooling device, and refrigerator
Technical Field
The present invention relates to a refrigerant compressor mainly used for a household electric refrigerator.
Background
In recent years, from the viewpoint of global environmental protection, efficient compressors that reduce the use of fossil fuels have been actively developed.
In a conventional compressor, one of sliding members constituting a sliding portion is formed of a sliding material obtained by subjecting an iron-based material subjected to nitriding treatment to manganese phosphate treatment, and the other sliding member is formed of an aluminum die-cast product subjected to anodizing treatment (see, for example, japanese patent application laid-open No. 6-117371).
FIG. 14 is a sectional view showing a conventional refrigerant compressor disclosed in Japanese patent application laid-open No. 6-117371. As shown in fig. 14, the sealed container 1 stores oil 2 at the bottom, and accommodates an electric motor unit 5 including a stator 3 and a rotor 4, and a reciprocating compressor unit 6 driven by the electric motor unit.
Next, the compression unit 6 will be described in detail.
The crankshaft 7 is composed of a main shaft 8 into which the rotor is press-fitted and fixed and an eccentric shaft 9 formed eccentrically with respect to the main shaft 8, and the crankshaft 7 isprovided with an oil feed pump 10. The cylinder block 11 is formed with a compression chamber 13 formed by a substantially cylindrical hole 12, and is provided with a bearing portion 14 that pivotally supports the main shaft portion 8.
The piston 15 loosely fitted in the hole 12 is connected to a connecting rod 17 as a connecting mechanism between the piston 15 and the eccentric shaft 9 via a piston pin 16. The end face of the bore 12 is sealed by a valve plate 18.
The hydraulic cylinder head 19 forms a high pressure chamber and is fixed to the valve plate 18 on the side opposite to the hole 12. The suction pipe 20 is fixed to the closed casing 1, is connected to a low-pressure side (not shown) of the refrigeration cycle, and introduces a refrigerant gas (not shown) into the closed casing 1. Suction muffler 21 is sandwiched between valve plate 18 and cylinder head 19.
The main shaft portion 8 and the bearing portion 14 of the crankshaft 7, the piston 15 and the hole 12, the piston pin 16 and the connecting rod 17, and the eccentric shaft 9 and the connecting rod 17 of the crankshaft 7 form sliding portions with each other. One of the sliding members constituting the sliding portion is formed of a sliding material obtained by subjecting a nitrided iron-based material to manganese phosphate treatment, and the other sliding member is formed of an anodized aluminum die-cast member.
Next, the above-described configuration will be described. Electric power supplied from a commercial power source (not shown) is supplied to the electric unit 5, and the rotor 4 of the electric unit 5 is rotated. The rotor 4 rotates the crankshaft 7, and the eccentric motion of the eccentric shaft 9 drives the piston 15 from a connecting rod 17 as a coupling mechanism via a piston pin 16. Thereby, the piston 15 reciprocates in the bore 12, and the refrigerant gas introduced into the sealed container 1 through the suction pipe 20 is sucked from the suction muffler 21 and continuously compressed in the compression chamber 13.
The oil 2 is supplied from the oil supply pump 10 to each sliding portion to lubricate the sliding portion in accordance with the rotation of the connecting rod 7, and the supplied oil 2 functions as a seal between the piston 15 and the hole 12.
In order to reduce leakage losses, the piston 15 and the bore 12 are loosely fitted with a very small clearance. As a result, a portion where the piston 15 and the hole 12 locally come into contact with each other may be generated due to an error in shape or accuracy. However, since one of the sliding members of the sliding portion is subjected to the manganese phosphate treatment having low hardness and low density, even if the sliding members come into contact with each other, the manganese phosphate at the portion is worn away and can be adapted to the shape of the other (initial running-in). Therefore, the sliding loss can be reduced at the sliding portion between the piston 15 and the bore 12.
In the refrigerant compressor described in the above-mentioned japanese unexamined patent publication No. 6-117371, since the manganese phosphate treatment having low hardness and low density is applied to one of the sliding members of the sliding portion, the initial running-in property is good. However, for example, when the sliding portions are repeatedly brought into contact with each other while an oil film is not formed in the sliding portions at the time of startup or the like, the manganese phosphate layer is worn away by abrasion, and metal contact may occur between the base materials. As a result, in the refrigerant compressor, the friction coefficient increases, the sliding loss increases, and further, if the amount of heat generation increases, there is a possibility that the wear increases and abnormal wear occurs.
In particular, if abrasion occurs between the piston 15 and the bore 12, a gap therebetween becomes large, and the compressed refrigerant gas leaks from the gap between the piston 15 and the bore 12, which may reduce efficiency.
In addition, the metal powder generated by the abrasion reacts with the oil degradation product to form sludge derived from the metal salt. This sludge adheres to the inner wall of a capillary tube or an expander having a fine path, which is generally used as an expander in a cooling system, and may cause an obstacle to the refrigerant circulation.
As another conventional technique, there is a technique of: as a sliding material for a compressor, molybdenum disulfide (MoS) as a solid lubricant is formed on the surface of a sliding part2) A solid-solution mixed layer (see, for example, international publication No. 04/055371 manual).
Fig. 15 is a cross-sectional view of a conventional mixed layer containing molybdenum disulfide as a solid solution, as described in international publication No. 04/055371.
As shown in fig. 15, in the compression unit having the sliding component made of the metal material, a mixed layer 33 in which molybdenum disulfide is bonded is formed on the sliding surface of the sliding component. Therefore, even when the piston 15 is brought into zero at the top dead center and the bottom dead center to cause metal contact with the hole 12, the friction coefficient can be reduced and the sliding loss can be reduced by the solid lubricity of the molybdenum disulfide in the mixed layer 33 formed on the surface of the piston 15. Further, by forming the fine dimples 34 on the surface of the sliding portion, the fine dimples 34 function as a labyrinth seal during compression, thereby making it possible to reduce leakage loss and improve wear resistance.
In the method described in the above-mentioned international publication No. 04/055371, even if solid contact occurs, the molybdenum disulfide in the mixed layer 33 cracks at a low friction coefficient, and thus the self-lubricating effect can be exhibited. However, in this method, since the mixed layer has a hardness close to that of the base material, an effect of initial running-in is hardly obtained, and therefore, there is a problem that the sliding loss cannot be reduced and the compressor efficiency is lowered.
Further, although the self-lubricating effect is exhibited, there is still a problem that a metal salt is generated from a metal powder when the mixed layer or the counter sliding surface is worn.
Here, it is considered that both advantages can be obtained by forming a mixed layer in which molybdenum disulfide is dissolved by the method described in international publication No. 04/055371 on a sliding surface and further performing manganese phosphate treatment by the method described in japanese unexamined patent publication No. 6-117371 on the mixed layer. However, when the manganese phosphate treatment is performed on the mixed layer, the sliding surface is corroded, and the mixed layer in which molybdenum disulfide is dissolved is corroded according to the following chemical reaction formulas (chemical formula 1), (chemical formula 2), and (chemical formula 3) of the manganese phosphate treatment. Therefore, it is almost impossible to realize the above-described structure.
(chemical formula 1)
(chemical formula 2)
(chemical formula 3)
Here, Me is a 2-valent metal salt (Fe, Mn).
Me(H2PO4)2: no. 1 phosphate, MeHPO4: 2 phosphoric acid salt, Me3(PO4)2: no. 3 phosphate salt
Disclosure of Invention
The present invention has been made to solve the above-described conventional problems, and an object of the present invention is to provide a highly reliable and highly efficient refrigerant compressor capable of reducing a sliding loss.
In order to solve the above-described conventional problems, a refrigerant compressor according to the present invention is configured such that a mixed layer in which molybdenum disulfide is dissolved in a solid solution is formed on at least one sliding surface of a sliding component made of a metal material, and a single layer of molybdenum disulfide is formed on a surface of the mixed layer. Thus, the molybdenum disulfide of the monomer layer has the following effects: initial running-in occurs, sliding loss is reduced, friction between the base material and the mixed layer or between the base material and the opposite sliding surface is suppressed, and generation of metal powder is prevented. Further, in the refrigerant compressor of the present invention, even if the single layer is peeled off, the structure of molybdenum disulfide in the mixed layer is a close-packed hexagonal crystal, and therefore, the following effects are obtained: even if solid contact occurs, molybdenum disulfide cracks at a low friction coefficient to exhibit a solid lubrication effect, thereby reducing the friction coefficient of the sliding portion and the sliding loss.
In the refrigerant compressor of the present invention, as described above, the mixed layer in which molybdenum disulfide is dissolved in a solid solution is formed on the sliding surface, and the single layer of molybdenum disulfide is formed on the surface of the mixed layer, whereby the friction coefficient can be reduced, and the refrigerant compressor with high reliability and high efficiency can be provided. In the refrigerant compressor of the present invention, since the generation of metal abrasion powder in the mixed layer, the base material, and the counter sliding surface can be suppressed, the generation of metal salt due to the metal abrasion powder and the deteriorated oil is reduced, and even if a fine path such as a capillary tube or an expander in the refrigerant path is provided, the clogging due to the metal salt in the fine path can be prevented.
A first aspect of the present invention provides a refrigerant compressor including a compression unit having a sliding component made of a metal material, wherein a mixed layer in which molybdenum disulfide is dissolved is formed on at least one sliding surface of the sliding component, and a single layer of molybdenum disulfide is formed on a surface of the mixed layer. Thus, the first aspect of the present invention has the following effects based on the molybdenum disulfide of the monomer layer: due to the self-lubricating effect of the molybdenum disulfide, the friction coefficient is reduced, and the sliding loss is reduced. In the first aspect of the present invention, even if the monomer layer peels off, the molybdenum disulfide in the mixed layer has a close-packed hexagonal structure, and therefore, even if solid contact occurs, the molybdenum disulfide cracks at a low friction coefficient, and a solid lubrication effect is exerted. Thus, since the friction coefficient of the sliding portion is reduced and the sliding loss is reduced, according to the first aspect of the present invention, it is possible to provide a highly reliable and highly efficient refrigerant compressor in which metal abrasion of the mixed layer, the base material, and the counter sliding surface can be suppressed.
In the second aspect of the present invention, the maximum concentration of molybdenum disulfide in the mixed layer is set to 5 wt% or more, so that the self-lubricity of molybdenum disulfide in the mixed layer is stabilized, and the friction coefficient is further reduced. Therefore, according to the second aspect of the present invention, in addition to the effects of the first aspect of the present invention, it is possible to provide a highly reliable and highly efficient refrigeration compressor in which metal abrasion of the mixed layer, the base material, and the counter sliding surface can be further suppressed.
In the third aspect of the present invention, in addition to the first aspect of the present invention, if the thickness of the mixed layer is 0.1 μm to 2.0 μm and the thickness of the mixed layer is secured to 0.1 μm to 2.0 μm, the solid lubrication action of the molybdenum disulfide in the mixed layer can be stably exerted. Therefore, the third aspect of the present invention can reduce the friction coefficient of the sliding portion and reduce the sliding loss. Therefore, according to the third aspect of the present invention, in addition to the effects of the first aspect of the present invention, it is possible to provide a highly reliable and highly efficient refrigerant compressor in which metal abrasion of the mixed layer, the base material, and the counter sliding surface can be further suppressed.
In the fourth aspect of the present invention, in addition to the first aspect of the present invention, the molybdenum disulfide forming the molybdenum disulfide monomer layer has a purity of 98% or more, and since impurities having a higher friction coefficient than molybdenum disulfide are usually present in an extremely small amount, the friction coefficient of the molybdenum disulfide monomer layer can be reduced, and the sliding loss can be reduced.Therefore, according to the fourth aspect of the present invention, in addition to the effects of the first aspect of the present invention, it is possible to provide a highly reliable and highly efficient refrigerant compressor in which metal abrasion of the mixed layer, the base material, and the counter sliding surface can be further suppressed.
In the fifth aspect of the present invention, in addition to the first aspect of the present invention, if the thickness of the molybdenum disulfide single layer is 0.1 μm to 2.0 μm, and if the thickness of the single layer is 0.1 μm to 2.0 μm when the single layer is peeled off, the amount of leakage from the piston/hole in particular does not increase extremely, and therefore the cooling capacity does not decrease. Therefore, according to the fifth aspect of the present invention, on the basis of the first aspect of the present invention, it is possible to provide a further high-efficiency refrigerant compressor.
A sixth aspect of the present invention is, in addition to any one of the first to fifth aspects of the present invention, a compression unit that stores oil in a sealed container and accommodates the compression unit, the compression unit forming a reciprocating compression unit, the compression unit including: a crankshaft having a main shaft and an eccentric shaft; a thrust portion having one end integrally formed with the crankshaft and the other end integrally formed with a bearing portion; a bearing portion for rotatably supporting the main shaft; a hydraulic cylinder body forming a hydraulic cylinder; a piston reciprocating within the hydraulic cylinder; and a connecting rod disposed parallel to the eccentric shaft and connecting a piston pin fixed to the piston, the eccentric shaft, and the piston, wherein the sliding component made of a metal material is at least one of the crankshaft, the thrust portion, the cylinder block, the piston pin, and the connecting rod. Therefore, in the sixth aspect of the present invention, the molybdenum disulfide in the monomer layer has an effect of causing initial running-in and reducing sliding loss, and even if the monomer layer peels off, the molybdenum disulfide in the mixed layer is cracked at a low friction coefficient by solid contact because the structure of the molybdenum disulfide is hexagonal close-packed, and a solid lubrication effect is exerted. Therefore, the sixth aspect of the present invention can provide a refrigerant compressor having a reciprocating compression unit with high reliability and high efficiency, which can suppress metal abrasion of the mixed layer, the base material, and the counter sliding surface, and has an effect of reducing the friction coefficient of the sliding portion and reducing the sliding loss.
A seventh aspect of the present invention is, in any one of the first to fifth aspects of the present invention, a compression unit that stores oil in a sealed container and accommodates the compression unit, the compression unit including: a crankshaft having a main shaft and an eccentric shaft; a thrust portion having one end integrally formed with the crankshaft and the other end integrally formed with a bearing portion; a bearing portion for rotatably supporting the main shaft; a hydraulic cylinder body forming a hydraulic cylinder; a piston reciprocating within the hydraulic cylinder; and a connecting rod having a ball fixed to a side connected to the piston, wherein the piston forms a reciprocating compression unit in which the ball is fixed by caulking, and the sliding component made of a metal material is at least one of the crankshaft, the thrust portion, the cylinder block, the piston, and the connecting rod. Therefore, in the seventh aspect of the present invention, the molybdenum disulfide in the monomer layer has an effect of causing initial running-in and reducing sliding loss, and even if the monomer layer peels off, the molybdenum disulfide in the mixed layer has a close-packed hexagonal structure, and therefore, even if solid contact occurs, the molybdenum disulfide cracks at a low friction coefficient, and a solid lubrication effect is exerted. Thus, the present invention has the effect of reducing the friction coefficient of the sliding portion and the sliding loss, and therefore, according to the seventh aspect of the present invention, it is possible to provide a refrigerant compressor having a reciprocating compression unit which can suppress metal abrasion of the mixed layer, the base material, and the counter sliding surface, and which can prevent floating obstacle due to the reduction in the amount of metal abrasion powder entering and biting into the caulking portion of the piston and the ball, and which has high reliability and high efficiency.
An eighth aspect of the present invention is, in addition to any one of the first to fifth aspects of the present invention, a rotary plunger type compression unit that stores oil in a sealed container and accommodates a compression unit, the compression unit forming the rotary plunger type compression unit, the rotary plunger type compression unit comprising: a shaft having an eccentric portion; a hydraulic cylinder forming a compression chamber concentric with a rotation center of the shaft; a rotary plunger fitted to the eccentric portion and rolling in the compression chamber; a vane for dividing the inside of the compression chamber into a high pressure side and a low pressure side by being pressed against the rotary plunger; a main bearing that seals both side surfaces of the hydraulic cylinder and that axially supports a motor unit side of the shaft and a sub-bearing on an opposite side of the motor unit side; an oil supply spring fixed to one end of the shaft; and an oil supply pipe that houses the oil supply spring and has one end that opens into the oil, wherein the sliding component made of a metal material is at least one of the shaft,the hydraulic cylinder, the rotary plunger, the blade, the main bearing, the sub bearing, the oil supply spring, and the oil supply pipe. Therefore, in the eighth aspect of the present invention, the molybdenum disulfide in the monomer layer has an effect of causing initial running-in and reducing sliding loss, and even if the monomer layer peels off, the molybdenum disulfide in the mixed layer has a close-packed hexagonal structure, and therefore, even if solid contact occurs, the molybdenum disulfide cracks at a low friction coefficient, and a solid lubrication effect is exerted. Therefore, the eighth aspect of the present invention can provide a refrigerant compressor having a rotary compression unit with high reliability and high efficiency, in which the friction coefficient of the sliding portion is reduced and the sliding loss is reduced, and which can suppress metal abrasion of the mixing layer, the base material, and the counter sliding surface.
A ninth aspect of the present invention is a cooling device including the refrigerant compressor, the capillary tube, and the expansion valve according to any one of the first to eighth aspects of the present invention in an expander. In the ninth aspect of the present invention, since the amount of metal abrasion powder discharged from the compressor is small, the amount of metal salt adhering to the inner surface of the capillary tube or the fine path of the expansion valve, which is the fine path, due to the metal abrasion powder and the deteriorated oil is reduced, and it is possible to provide a highly reliable cooling device which prevents the refrigerant circulation from being inhibited.
The tenth aspect of the present invention is used in a refrigerator for household use, for example, which employs at least one of a fine capillary tube and an expansion valve, as compared with a general refrigerator warehouse or a service refrigerator having a large refrigerant circulation amount. In the tenth aspect of the present invention, since the cooling device according to the ninth aspect of the present invention is provided, the amount of metal abrasion powder discharged from the compressor is small, and therefore, the amount of metal salt adhering to the inner surface of the capillary tube or the fine path of the expansion valve, which is the fine path, due to the metal abrasion powder and the deteriorated oil is reduced, and it is possible to provide a refrigerator for home use, for example, which can prevent the refrigerant circulation from being inhibited and has high reliability.
Drawings
Fig. 1 is a sectional view of a refrigerant compressor in embodiment 1 of the present invention;
FIG. 2 is an enlarged view of portion A of FIG. 1;
FIG. 3 is an enlarged view of portion B of FIG. 2;
fig. 4 is a diagram of the formation of molybdenum disulfide according to embodiment 1 of the present invention;
fig. 5 is a characteristic diagram showing a relationship between a piston/bore clearance and a cooling capacity in embodiment 1 of the present invention;
fig. 6 is a concentration profile of molybdenum disulfide according to embodiment 1 of the present invention;
fig. 7 is a characteristic diagram showing the relationship between the concentration of molybdenum disulfide and the efficiency in embodiment 1 of the present invention;
fig. 8 is an assembly view of a connecting rod according to embodiment 1 of the present invention in which a ball is fixed by caulking and floating;
fig. 9 is a configuration diagram of a household refrigerator according to embodiment1 of the present invention;
fig. 10 is a sectional view of the expander according to embodiment 1 of the present invention;
fig. 11 is a sectional view of a refrigerant compressor according to embodiment 2 of the present invention;
FIG. 12 is a cross-sectional view taken along line C-D of FIG. 11;
fig. 13 is an enlarged view of a portion E of fig. 12;
fig. 14 is a sectional view of a conventional refrigerant compressor;
fig. 15 is a sectional view of a conventional mixed layer in which molybdenum disulfide is dissolved.
Detailed Description
(embodiment mode 1)
Fig. 1 is a sectional view of a refrigerant compressor according to embodiment 1 of the present invention, fig. 2 is an enlarged view of a portion a in fig. 1, fig. 3 is an enlarged view of a portion B in fig. 2, fig. 4 is a diagram showing formation of molybdenum disulfide according to the embodiment, fig. 5 is a characteristic diagram showing a relationship between a piston/hole gap and cooling capacity according to the embodiment, fig. 6 is a concentration profile of molybdenum disulfide according to the embodiment, fig. 7 is a characteristic diagram showing a relationship between a concentration and efficiency of molybdenum disulfide according to the embodiment, fig. 8 is a link assembly diagram showing a ball fixed to a link by caulking of a piston according to the embodiment, fig. 9 is a structural diagram of a household refrigerator according to the embodiment, and fig. 10 is a sectional view of an expansion valve according to embodiment 1.
In fig. 1, 2, and 3, refrigerant gas 102 made of R600a is filled in sealed container 101, and oil 103 is stored in thebottom of sealed container 101. Sealed container 101 accommodates electric motor unit 106 including stator 104 and rotor 105, and reciprocating compressor unit 107 driven by the electric motor unit.
Next, the compression section 107 will be described in detail.
Crankshaft 108 has a main shaft 109 for pressing and fixing rotor 105 and an eccentric shaft 110 formed eccentrically to main shaft 109. An oil supply pump 111 communicating with oil 103 is provided at a lower end of crankshaft 108. The cylinder block 112 made of cast iron is formed with a substantially cylindrical hole 113 and a bearing portion 114 for pivotally supporting the main shaft 109.
Further, the rotor 105 is formed with a flange surface 120, and an upper end surface of the bearing portion 114 is a thrust portion 122. A thrust washer 124 is inserted between the flange surface 120 and the thrust portion 122 of the bearing portion 114. The flange surface 120, the thrust portion 122, and the thrust washer 124 constitute a thrust bearing portion 126.
The piston 132 loosely fitted into the hole 113 so as to maintain a certain amount of clearance is made of an iron-based material, forms a compression chamber 134 together with the hole 113, and is connected to the eccentric shaft 110 via a piston pin 137 by a connecting rod 138 as a connecting member. The end face of hole 113 is sealed by valve plate 139.
Hydraulic cylinder head 140 forms a high pressure chamber and is fixed to valve plate 139 on the side opposite to hole 113. A suction pipe (not shown) is fixed to the closed casing 101, is connected to a low-pressure side (not shown) of the refrigeration cycle, and introduces the refrigerant gas 102 into the closed casing 101. Suction muffler 142 is sandwiched between valve plate 139 and cylinder head 140.
The piston 132 and the hole 113, the main shaft 109 and the bearing portion 114, the thrust portion 122 and the thrust washer 124, the piston pin 137 and the connecting rod 138, and the eccentric shaft 110 and the connecting rod 138 form sliding portions with each other. A mixed layer 150 in which molybdenum disulfide is solid-dissolved on the surface of the base material, and a molybdenum disulfide single layer 160 further formed on the surface of the mixed layer 150 are formed on at least one of the sliding portions.
Here, the piston 132 will be described in detail as an example.
In the sliding portion formed between the piston 132 and the hole 113, a mixed layer 150 in which molybdenum disulfide is solid-dissolved on the surface of an iron-based material as a base material, and a single layer 160 of molybdenum disulfide further formed on the surface of the mixed layer 150 are formed on the surface of the sliding portion of the piston 132. More preferably: the purity of molybdenum disulfide is set to 98% or more, the thickness of the molybdenum disulfide single layer 160 is set to 0.1 to 2.0 μm, the thickness of the mixed layer 150 is set to 0.1 to 2.0 μm, and the maximum concentration of molybdenum disulfide in the mixed layer 150 is set to 5 to 50 wt%.
As a method for forming the mixed layer 150 in which molybdenum disulfide is dissolved in a solid solution and the single layer 160 of molybdenum disulfide further formed on the surface of the mixed layer 150, in embodiment 1 of the present invention, a method is employed in which molybdenum disulfide particles having a purity of 98% or more are caused to collide with a metal sliding surface as a base material of a sliding component at a certain speed or higher.
In this case, the projection pressure of molybdenum disulfide is preferably 1.0MPa to 1.5 MPa. By utilizing the thermal energy generated at the time of collision in this method, oxygen on the surface of the base material is diffused to form the monomer layer 160 of molybdenum disulfide, and by collision of molybdenum disulfide particles, a part of the particles are melted into the base material to form a metal bond, and it is known that the mixed layer 150 of molybdenum disulfide in solid solution and the monomer layer 160 of molybdenum disulfide can be formed at the same time.
In order to reduce the leakage loss, the piston 132 and the hole 113 are loosely fitted with a very small clearance, for example, a clearance having a diameter of about 5 μm to 15 μm.
The operation of the refrigerant compressor according to embodiment 1 configured as described above will be described.
Electric power supplied from a commercial power supply (not shown) is supplied to the electric unit 106, and the rotor 105 of the electric unit 106 is rotated. Rotation of rotor 105 rotates crankshaft 108, and eccentric shaft 110 performs eccentric motion. The eccentric motion of eccentric shaft 110 drives piston 132 from connecting rod 138 as a coupling mechanism via piston pin 137, thereby reciprocating piston 132 within hole 113. As a result, refrigerant gas 102 introduced into hermetic container 101 through a suction pipe (not shown) is sucked from suction muffler 142 and compressed in compression chamber 134.
Oil 103 is supplied from an oil supply pump 111 to each sliding portion in accordance with the rotation of the crankshaft 108, lubricates the sliding portion, and the supplied oil 113 functions as a seal between the piston 132 and the hole 113.
In this sliding operation, since the clearance between the piston 132 and the hole 113 is very small, a portion locally causing mutual contact may be generated due to errors in the shape and accuracy of the piston 132 and the hole 113. In embodiment 1, since molybdenum disulfide of the monomer layer 160 has a property of being very easily cracked, initial running-in property in conformity with the shape of the sliding partner is good. As a result, the molybdenum disulfide of the monomer layer 160 at the portions in contact with each other is abraded and worn, so that the sliding loss can be reduced, and a high-efficiency refrigerant compressor can be provided.
Here, the relationship between the amount of leakage from the piston 132 and the bore 113 and the cooling capacity will be described with reference to fig. 5.
The horizontal axis of fig. 5 represents the clearance between the piston 132 and the orifice 113, and the vertical axis represents the cooling capacity.
As is clear from the results shown in fig. 5, when the predetermined gap range is set to a to B μm, the cooling capacity rapidly decreases after exceeding B +4 μm.
Therefore, by forming the thickness of the monomer layer 160 on the sliding portion surface of the piston 132 to be 0.1 μm to 2.0 μm, even if the molybdenum disulfide monomer layer 160 peels off during operation, the clearance between the piston 132 and the bore 113 increases by only 4.0 μm at the maximum. As a result, in the configuration of embodiment 1, the amount of clearance between the piston 132 and the bore 113 is not extremely increased, and the cooling capacity is not extremely decreased, so that a refrigerant compressor having a high efficiency with more stability can be provided.
Next, in the refrigerant compressor according to embodiment 1 of the present invention, an effect of the molybdenum disulfide single layer 160 and the mixed layer 150 being formed will be described.
When the piston 132 is positioned at the top dead center and the bottom dead center, the speed is 0m/s, and theoretically, no oil pressure is generated and no oil film is formed. Therefore, metal contact is generated more at the top dead center and the bottom dead center.
In the refrigerant compressor, when the piston 132 is positioned near the top dead center, the piston 132 receives a large compression load by the compressed high-pressure refrigerant. This compression load is transmitted to crankshaft 108 via piston pin 137 and connecting rod 138, and crankshaft 108 is pressed and tilted by piston 132 near the top dead center. The inclination of crankshaft 108 causes piston 132 to be inclined in bore 113. As a result, one end of the upper end surface and the other end of the lower end surface of the piston 132 are jammed with the hole 113. Also, due to the seizing, the piston 132 slides with the bore 113 to generate abrasion. In particular, in the case of the refrigerant compressor having the one-arm bearing as in embodiment 1, the seizure becomes more pronounced because the inclination of the crankshaft 108 increases.
As a result, the molybdenum disulfide single layer 160 is worn away, and the mixed layer 150 is exposed on the surface, which may become a sliding surface.
In embodiment 1, the molybdenum disulfide of the mixed layer 150 has a close-packed hexagonal structure and a molecular size of about 6 × 10-4μ m, very small and thus crack with a low coefficient of friction. Therefore, even if metal contact is generated between the piston 132 and the bore 113, since the friction coefficient of the sliding portion is reduced, the sliding loss is reduced, and thus a highly reliable refrigerant compressor can be provided.
Fig. 6 shows the concentration distribution of molybdenum disulfide formed on the sliding portion surface of piston 132 used in embodiment 1 of the present invention.
For the measurement of the concentration of molybdenum disulfide formed on the sliding portion surface ofthe piston 132 in fig. 6, an energy dispersive X-ray analyzer is generally used. The energy dispersive X-ray analysis apparatus is briefly described.
Electrons irradiated from the energy-dispersive X-ray analyzer to the sliding portion of the piston 132 enter a certain depth from the surface of the sliding portion, and generate characteristic X-rays. The characteristic X-ray is generated by an X-ray that is unique to an element and has excess energy when an electron at a high energy level is moved by a vacancy formed by the electron rotating around a nucleus and being pushed out of an atom by the electron entering a certain depth.
The energy dispersion type X-ray analyzer can analyze the structural elements on the sliding portion surface of the piston 132 by using the characteristic X-ray, and thus can measure the concentration of molybdenum disulfide formed on the sliding portion surface. The maximum concentration of molybdenum disulfide for the mixed layer 150 can be obtained near its outermost surface, and thus the maximum concentration can be detected by measuring here.
As shown in FIG. 6, the thickness of the mixed layer 150 containing molybdenum disulfide is 0.1 to 2.0 μm, and the maximum concentration is 5 to 20 wt%. In this way, when the mixed layer 150 of molybdenum disulfide is formed, the self-lubricity of molybdenum disulfide is stabilized, and the friction coefficient is further reduced.
Next, the maximum concentration of molybdenum disulfide in the mixed layer 150 and the efficiency of the refrigerant compressor will be described in detail with reference to fig. 7. Fig. 7 shows the maximum concentration of molybdenum disulfide for the mixed layer 150 of fig. 3 as a function of refrigerant compressor efficiency (c.o.p.: efficiency coefficient). In the refrigerant compressor, as described above, the inclined piston 132 moves in the hole 113, and one end of the upper end surface and the other end of the lower end surface of the piston 132 are engaged with the hole 113, whereby the mixed layer 150 of the piston 132 serves as a sliding surface.
As shown in fig. 7, if the maximum concentration of molybdenum disulfide in the mixed layer 150 exceeds 5 wt%, the efficiency of the refrigerant compressor is drastically improved. When the amount exceeds 15 wt%, the efficiency of the refrigerant compressor becomes substantially constant. Therefore, if the maximum concentration of molybdenum disulfide in the mixed layer 150 is ensured to be 5 wt% or more at the lowest, the self-lubricity of molybdenum disulfide can be considered to be stable.
On the other hand, in order to increase the maximum concentration of molybdenum disulfide in the mixed layer 150, it is necessary to cause a large amount of molybdenum disulfide particles, which are particles of molybdenum disulfide, to collide with the metal sliding surface for a long period of time. Therefore, considering the cost and productivity of molybdenum disulfide, the maximum concentration of molybdenum disulfide is limited to 20 wt% in practical use.
Therefore, in embodiment 1, the maximum concentration of molybdenum disulfide in the mixed layer 150 is controlled to be between 5 wt% and 20 wt%.
In embodiment 1 of the present invention, a compressor of a constant speed is described above. With the development of inverters, the speed of refrigerant compressors is being lowered, and particularly in ultra-low speed operation limited to 20Hz, fluid lubrication is more difficult to achieve and metal contact is more likely to occur, so that the effect of the present invention is more remarkable.
In embodiment 1 of the present invention, a mixed layer 150 in which molybdenum disulfide is dissolved in a solid solution is formed on the surface of the slidingportion of the piston 132, and a single layer 160 of molybdenum disulfide is formed on the surface of the mixed layer 150. However, in the refrigerant compressor of the present invention, the mixed layer 150 and the single layer 160 of molybdenum disulfide may be formed on the sliding portion surface on the side of the bore 113, or may be formed on both the piston 132 and the bore 113. By forming the mixed layer 150 and the single layer 160 of molybdenum disulfide on both sliding portions in this manner, higher wear resistance can be obtained.
In embodiment 1 of the present invention, a mixed layer 150 in which molybdenum disulfide is dissolved is formed on the surface of the sliding portion of the piston 132, and a single layer 160 of molybdenum disulfide is further formed on the surface of the mixed layer 150. However, the same excellent effect can be obtained even if the mixed layer 150 and the single layer 160 of molybdenum disulfide are formed on the sliding portions of the main shaft 109 and the bearing portion 114 of the crankshaft 108, the flange surface 120 and the thrust washer 124 of the rotor 105, the upper end surface thrust portion 122 and the thrust washer 124 of the bearing portion 114, the piston pin 137 and the connecting rod 138, and the eccentric shaft 110 and the connecting rod 138, which mutually form the sliding portions.
Although embodiment 1 of the present invention has been described by taking an example in which the thrust bearing portion 126 is constituted by the flange surface 120, the thrust portion 122, and the thrust washer 124, the same excellent effects can be obtained even when the thrust bearing is formed by the thrust surface 172 of the crankshaft 108 and the thrust portion 122 of the bearing portion 114 provided on the opposite side of the eccentric shaft 110 side of the flange portion 170 between the main shaft 109 and the eccentric shaft 110 of the crankshaft 108.
Further, a connecting rod 183 to which the ball 182 is fixed is provided on the side connected to the piston 181 shown in fig. 8, and the piston 181 is configured such that the ball 182 is caulked and fixed to float. In general, in a connection method called a ball joint, the amount of metal abrasion powder entering and biting into the caulking floating fixing portion is reduced, whereby floating failure can be prevented, and high efficiency at the initial stage of manufacturing can be maintained with high reliability.
Fig. 8 shows a state in which the resin 184 is sandwiched as an intermediate material for smoothing the sliding between the piston 181 and the ball 182.
The expander of the domestic refrigerator shown in fig. 9 uses a capillary tube 188. In order to ensure the forster performance in Japanese Industrial Standard (JIS) for the temperature of the freezing chamber, the pressure reduction amount of the capillary tube 188 is increased by keeping-18 ℃, i.e., the inner diameter thereof is designed to be smaller than 1mm so that the temperature of the evaporator 196 is about-30 ℃. The adhesion of foreign matter to the fine path represented by the capillary tube 188 or the refrigerant path in the high-temperature compressor 197 is a large cause of a reduction in cooling capacity. Therefore, in a household refrigerator which is a durable consumer product for 10 years or longer, the mixing of foreign matters during production is strictly limited, and the refrigerant, the oil purity, the residual water content, the processing oil, and the like are set. Further, since the residual air causes the generation of foreign matter by oxidation, the vacuum is evacuated to a high vacuum, and the refrigerant is hermetically sealed.
Next, the flow of the refrigerant will be described. The refrigerant is compressed by the compressor 197, dissipates heat by the condenser 198, is reduced in pressure by the capillary tube 188, absorbs heat in the refrigerator 199 by the evaporator 196, and circulates through the compressor 197.
Since the refrigerant flows in a complicated manner in a mixed flow of gas and liquid through an inlet (not shown) and an outlet (not shown) of the capillary tube, foreign matter that is difficult to dissolve in oil usually adheres to the inlet or the outlet, and the circulation of the refrigerant is inhibited. In the household refrigerator 195 of embodiment 1, since the contamination of foreign substances during manufacturing is strictly limited, foreign substances hardly adhere to the inlet or outlet of the capillary tube. In the household refrigerator having such a configuration, the amount of metal abrasion powder is small, and accordingly, the amount of metal salt generated by the metal abrasion powder and the deteriorated oil adhering to the refrigerant path is also reduced, and accordingly, foreign matters adhering to the refrigerant path can be controlled to be extremely small, and thus, a highly reliable household refrigerator can be provided without reducing the refrigerant circulation amount.
Although the capillary tube 188 is used in embodiment 1, even in the case where the expander 189 as illustrated in fig. 10 is used, the refrigerant circulation failure due to the adhesion of foreign matter to the valve seat surface 190 can be prevented, and an excellent effect can be achieved.
(embodiment mode 2)
Fig. 11 is a sectional view of a refrigerant compressor according to embodiment 2 of the present invention, fig. 12 is a sectional view taken along line C-D in fig. 11, and fig. 13 is an enlarged view of portion E in fig. 12.
In fig. 11, 12, and 13, an electric unit 204 including a stator 202 and a rotor 203, and a rotary plunger type compression unit 205 driven by the electric unit 204 are housed in a sealed container 201 together with oil 206.
The compression unit 205 includes: a shaft 210 having an eccentric portion 207, a main shaft portion 208, and a sub shaft portion 209; a hydraulic cylinder 212 forming a compression chamber 211; a main bearing 213 and a sub bearing 214 that seal both end surfaces of the hydraulic cylinder 212 and respectively support the main shaft portion 208 and the sub shaft portion 209; a rotary plunger 215 loosely fitted in the eccentric portion 207 and rolling in the compression chamber 211; and a plate-like vane 216 that is inserted into and pressed against the rotary plunger 215 and divides the compression chamber 211 into a high pressure side and a low pressure side. A rotor 203 is fixed to the main shaft portion 208.
The oil pump 217 fixed to the sub-bearing 214 is composed of an oil supply pipe 220 and an oil supply spring 222 loosely fitted to the oil supply pipe 220. The oil feed pump 217 feeds the oil 206 to sliding portions formed by the eccentric portion 207 and the rotary plunger 215, the main shaft portion 208 and the main bearing 213, and the sub shaft portion 209 and the sub bearing 214, respectively.
In embodiment 2, a mixed layer 224 in which molybdenum disulfide is dissolved is formed on a base iron (Fe) material which is a sliding surface of the eccentric portion 207 of the shaft 210, the main shaft portion 208, and the auxiliary shaft portion 209, and a single layer 228 of molybdenum disulfide is further formed on a surface of the mixed layer 224.
More preferably, the purity of molybdenum disulfide is set to 98% or more, the thickness of the molybdenum disulfide single layer 228 is set to 0.1 to 2.0 μm, the thickness of the mixed layer 224 is set to 0.1 to 2.0 μm, and the maximum concentration of molybdenum disulfide of the mixed layer 224 is set to 5 to 50 wt%.
The operation of the refrigerant compressor according to embodiment 2 configured as described above will be described.
As the rotor 203 rotates, the shaft 210 rotates, and the rotary plunger 215 loosely fitted on the eccentric portion 207 rotates in the compression chamber 211. Thereby, the space on the high-pressure side and the space on the low-pressure side of the compression chamber 211 continuously change in volume, and the refrigerant gas is continuously compressed. The compressed refrigerant gas is discharged into sealed container 201, and a high-pressure atmosphere is formed in sealed container 201. Further, since the inside of the closed casing 201 is at a high pressure, the atmospheric pressure in the closed casing 201 acts on the vane 216 as a back pressure, and the tip of the vane 216 is pressed against the outer peripheral surface of the rotary plunger 215.
Further, the oil supply spring 222 loosely fitted to the oil supply pipe 220 continuously supplies the oil 206 to each sliding portion as the shaft 210 rotates.
In the rotary piston type refrigerant compressor, since the rotary piston 215 is rotatably loosely fitted to the eccentric portion 207, the relative speed between the rotary piston 215 and the eccentric portion 207 is smaller than the relative speed between the main shaft portion 208 and the main bearing 213, and between the sub shaft portion 209 and the sub bearing 214. This is because the soxhlet number S (formula 1) representing the journal bearing characteristics, which is obtained from the bearing radius R, the radial clearance C, the speed N, the oil viscosity μ, and the surface pressure P, is reduced, and this is a disadvantageous condition that metal contact is likely to occur in the sliding lubrication.
mu.XN/Px (R/C)2 (formula 1)
In the rotary plunger type refrigerant compressor, since the inside of the closed casing 201 is usually at a condensation pressure, the internal pressure is high, and the refrigerant is easily dissolved in the oil 206. This is because the viscosity of the oil is reduced, and the aforementioned soxhlet number S (formula 1) indicating the characteristics of the journal bearing is reduced, which is an unfavorable condition in terms of sliding lubrication.
However, by forming the mixed layer 224 in which molybdenum disulfide is solid-dissolved on the sliding portion surfaces of the eccentric portion 207 of the shaft 210, the main shaft portion 208, and the auxiliary shaft portion 209, and further forming the single layer 228 of molybdenum disulfide on the surface of the mixed layer 224, even under unfavorable conditions in terms of sliding lubrication where the sorafe number S (expression 1) is reduced, the molybdenum disulfide of the single layer 228 has a property of being very likely to crack, and therefore, the initial running-in property in conformity with the shape of the mating sliding surface is good. As a result, since the molybdenum disulfide of the monomer layer 228 at the contact portion is worn and worn, the rotary plunger type refrigerant compressor can provide a high-efficiency refrigerant compressor in which the sliding loss can be reduced.
In addition, even if contact is further generated between the sliding portions, the monomer layer 228 is abraded and peeled off, and since the structure of the molybdenum disulfide of the mixed layer 224 is a close-packed hexagonal crystal, the size of the molecule is about 6 × 10-4μ m, very small, and therefore can also crack with a low coefficient of friction. Thus, even if metal contact occurs between the rotary plunger 215 and the eccentric portion 207, between the main shaft portion 208 and the main bearing 213, and between the sub shaft portion 209 and the sub bearing 214, the friction coefficient of the sliding portion is reduced, and the sliding loss is reduced. Therefore, according to the configuration of embodiment 2, a refrigerant compressor with high reliability can be provided.
Further, by setting the thickness of the mixed layer 224 to 0.1 μm to 2.0 μm and setting the maximum concentration of molybdenum disulfide in the mixed layer 224 to 5 wt% or more and 20 wt% or less, the self-lubricity of molybdenum disulfide is stabilized and the friction coefficient is further lowered. Therefore, the refrigerant compressor with higher reliability and high efficiency can be provided by the structure.
In embodiment 2 of the present invention, a mixed layer 224 in which molybdenum disulfide is dissolved is formed on the sliding surfaces of the eccentric portion 207, the main shaft portion 208, and the sub shaft portion 209, and a single layer 228 of molybdenum disulfide is further formed on the surface of the mixed layer 224, but the mixed layer 224 and the single layer 228 of molybdenum disulfide may be formed on the inner circumferential surface of the rotary plunger 215 and on the main bearing 213 and the sub bearing 214. Further, the mixed layer 224 and the single layer 228 of molybdenum disulfide may be formed on both the inner peripheral surfaces of the eccentric portion 207 and the rotary plunger 215, both the main shaft portion 208 and the main bearing 213, and both the sub shaft portion 209 and the sub bearing 214. This can provide the following excellent effects: by forming the mixed layer 224 and the single layer 228 of molybdenum disulfide at the sliding portion, a refrigerant compressor with higher reliability and higher efficiency can be provided.
Further, when a mixed layer 224 in which molybdenum disulfide is dissolved is formed on the surfaces of the sliding portions of the rotary plunger 215 and the vane 216, the main bearing 213 and the vane 216, the sub bearing 214 and the rotary plunger 215, thecylinder 212 and the vane 216, the cylinder 212 and the rotary plunger 215, and the oil supply pipe and the oil supply spring, which have the sliding portions formed with each other, and a single layer 228 of molybdenum disulfide is further formed on the surface of the mixed layer 224, the friction coefficient of each sliding portion is reduced, and a highly reliable and highly efficient refrigerant compressor can be provided.
In embodiment 2 of the present invention, a compressor of a constant speed is described above. The effect of the present invention is more remarkable because the speed of the refrigerant compressor is lowered as the inverter is developed, and the abnormal wear is more problematic particularly in the ultra-low speed operation of 20 Hz.
(availability in industry)
As described above, the refrigerant compressor of the present invention is widely applicable to a device using a refrigeration cycle because a mixed layer in which molybdenum disulfide is dissolved in a solid solution is formed on a sliding surface of a sliding component, and a single layer of molybdenum disulfide is further formed on a surface of the mixed layer, so that a friction coefficient can be reduced, and a highly reliable and highly efficient compressor can be provided.

Claims (10)

1. A refrigerant compressor is provided with a compression unit having a sliding component formed of a metal material, wherein a mixed layer in which molybdenum disulfide is dissolved is formed on at least one sliding surface of the sliding component, and a single layer of molybdenum disulfide is further formed on the surface of the mixed layer.
2. The refrigerant compressor according to claim 1, wherein the maximum concentration of molybdenum disulfide in the mixed layer is 5 wt% or more.
3. The refrigerant compressor according to claim 1, wherein the thickness of the mixed layer is 0.1 to 2.0 μm.
4. A refrigerant compressor as claimed in claim 1, wherein the purity of the molybdenum disulfide forming the molybdenum disulfide monomer layer is 98% or more.
5. A refrigerant compressor according to claim 1, wherein the thickness of the molybdenum disulfide monomer layer is 0.1 μm to 2.0 μm.
6. The refrigerant compressor according to any one of claims 1 to 5,
oil is stored in the closed container and the compression unit is accommodated,
the compression unit is a reciprocating compression unit, and the compression unit includes: a crankshaft having a main shaft and an eccentric shaft; a thrust portion having one end integrally formed with the crankshaft and the other end integrally formed with a bearing portion; a bearing portion for rotatably supporting the main shaft; a hydraulic cylinder body forming a hydraulic cylinder; a piston reciprocating within the hydraulic cylinder; and a connecting rod disposed in parallel with the eccentric shaft and connecting a piston pin fixed to the piston, the eccentric shaft, and the piston,
the sliding component formed of a metal material is at least any one of the crankshaft, the thrust portion, the hydraulic cylinder block, the piston pin, and the connecting rod.
7. The refrigerant compressor according to any one of claims 1 to 5,
oil is stored in the closed container and the compression unit is accommodated,
the compression unit includes: a crankshaft having a main shaft and an eccentric shaft; a thrust portion having one end integrally formed with the crankshaft and the other end integrally formed with a bearing portion; a bearing portion for rotatably supporting the main shaft; a hydraulic cylinder body forming a hydraulic cylinder; a piston reciprocating within the hydraulic cylinder; and a connecting rod having a ball fixed to one side connected to the piston,
the piston forms a reciprocating compression unit that floatingly secures the ball rivets,
the sliding component made of a metal material is at least one of the crankshaft, the thrust portion, the cylinder block, the piston, and the connecting rod.
8. The refrigerant compressor according to any one of claims 1 to 5,
oil is stored in the closed container and the compression unit is accommodated,
the compression unit forms a rotary plunger type compression unit, and the rotary plunger type compression unit comprises: a shaft having an eccentric portion; a hydraulic cylinder forming a compression chamber concentric with a rotation center of the shaft; a rotary plunger fitted to the eccentric portion and rolling in the compression chamber; a vane for dividing the inside of the compression chamber into a high pressure side and a low pressure side by being pressed against the rotary plunger; a main bearing that seals both side surfaces of the hydraulic cylinder and that axially supports a motor unit side of the shaft and a sub-bearing on an opposite side of the motor unit side; an oil supply spring fixed to one end of the shaft; an oil supply pipe which accommodates the oil supply spring and has one end opened in the oil,
the sliding component formed of a metal material is at least any one of the shaft, the hydraulic cylinder, the rotary plunger, the blade, the main bearing, the sub bearing, the oil supply spring, and the oil supply pipe.
9. A cooling device comprising an expander and at least one of the refrigerant compressor, the capillary tube, and the expansion valve according to any one of claims 1 to 8.
10. A refrigerator comprising a cooling device including at least one of the refrigerant compressor, the capillary tube, and the expansion valve according to any one of claims 1 to 8 in an expander.
CNA2006101516342A 2005-09-08 2006-09-07 Refrigerant compressor, cooling system and refrigerator Pending CN1928362A (en)

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EP1926912A1 (en) 2008-06-04
US20090136375A1 (en) 2009-05-28
KR20080042124A (en) 2008-05-14
CN200985869Y (en) 2007-12-05
WO2007029884A1 (en) 2007-03-15

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