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US20130195707A1 - Refrigerant Compressor - Google Patents

Refrigerant Compressor Download PDF

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Publication number
US20130195707A1
US20130195707A1 US13/815,000 US201113815000A US2013195707A1 US 20130195707 A1 US20130195707 A1 US 20130195707A1 US 201113815000 A US201113815000 A US 201113815000A US 2013195707 A1 US2013195707 A1 US 2013195707A1
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US
United States
Prior art keywords
rotary shaft
film
compressor
hardness
hard film
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.)
Abandoned
Application number
US13/815,000
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English (en)
Inventor
Yuko Kozuma
Mutsunori Matsunaga
Kouiti Imada
Yuichi Yanagase
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Hitachi Global Life Solutions Inc
Original Assignee
Hitachi Appliances Inc
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Hitachi Appliances Inc filed Critical Hitachi Appliances Inc
Assigned to HITACHI APPLIANCES, INC. reassignment HITACHI APPLIANCES, INC. ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: MATSUNAGA, MUTSUNORI, YANAGASE, YUICHI, IMADA, KOUITI, KOZUMA, YUKO
Publication of US20130195707A1 publication Critical patent/US20130195707A1/en
Abandoned legal-status Critical Current

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Classifications

    • 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
    • F04B39/0094—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 crankshaft
    • 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
    • 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
    • F04C18/02—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents
    • F04C18/0207—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents both members having co-operating elements in spiral form
    • F04C18/0215—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents both members having co-operating elements in spiral form where only one member is moving
    • 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
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/0042—Driving elements, brakes, couplings, transmissions specially adapted for pumps
    • F04C29/005—Means for transmitting movement from the prime mover to driven parts of the pump, e.g. clutches, couplings, transmissions
    • F04C29/0071—Couplings between rotors and input or output shafts acting by interengaging or mating parts, i.e. positive coupling of rotor and shaft
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/02—Parts of sliding-contact bearings
    • F16C33/04—Brasses; Bushes; Linings
    • F16C33/043—Sliding surface consisting mainly of ceramics, cermets or hard carbon, e.g. diamond like carbon [DLC]
    • 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
    • F04C2230/00—Manufacture
    • F04C2230/90—Improving properties of machine parts
    • F04C2230/91—Coating
    • 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
    • F04C2240/00—Components
    • F04C2240/50—Bearings
    • F04C2240/54—Hydrostatic or hydrodynamic bearing assemblies specially adapted for rotary positive displacement pumps or compressors
    • 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
    • F04C2270/00—Control; Monitoring or safety arrangements
    • F04C2270/16—Wear
    • 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
    • F05C2201/00—Metals
    • F05C2201/04—Heavy metals
    • F05C2201/0433—Iron group; Ferrous alloys, e.g. steel
    • F05C2201/0436—Iron
    • 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
    • F05C2251/00—Material properties
    • F05C2251/10—Hardness
    • 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
    • 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
    • F05C2253/20—Resin
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/02—Parts of sliding-contact bearings
    • F16C33/04—Brasses; Bushes; Linings
    • F16C33/20—Sliding surface consisting mainly of plastics

Definitions

  • the present invention relates to refrigerant compressors used for cooling or air conditioning purposes and particularly to an improvement in the bearing section of a refrigerant compressor.
  • Patent Document 1 As the prior-art technique for the lead-free sliding material formed mainly of PTFE, the one disclosed in Patent Document 1 can be given.
  • APF annual performance factors
  • An object of the invention is to obtain a refrigerant compressor that is capable of preventing seizure or galling at the bearing slide section and has high anti-wear properties.
  • the present invention provides a refrigerant compressor comprising: a compressor mechanism for compressing a refrigerant; a rotary shaft for driving the compressor mechanism; a plain bearing located either at a joint section between the rotary shaft and the compressor mechanism or at a support section supporting the rotary shaft or plain bearings located at both of the joint section and the support section, wherein the plain bearing(s) is/are formed of a lead-free resin-impregnated material capable of adsorbing wear particles, wherein the rotary shaft is formed of an iron material, and wherein a section of the rotary shaft that comes into contact with the plain bearing(s) is covered with a hard film of a hardness of 1,000 Hv or more.
  • the present invention has the effect of obtaining a refrigerant compressor that is capable of preventing seizure or galling at the bearing slide section and has high anti-wear properties.
  • FIG. 1 is a vertical cross section showing Embodiment 1 of the refrigerant compressor of the invention
  • FIG. 2 is an enlarged cross section near the plain bearings of FIG. 1 ;
  • FIG. 3 is a graph showing the relationship between the hardness of a hard film covering the rotary shaft and the bearing wear rate
  • FIG. 4 is a diagram illustrating a modification of FIG. 2 and an enlarged cross section corresponding to FIG. 2 ;
  • FIG. 5 is an enlarged cross section explaining an example in which a hard film is provided on a base material
  • FIG. 6 is an enlarged cross section explaining another example in which a hard film is provided on a base material.
  • FIG. 7 is an enlarged cross section explaining a still another example in which a hard film is provided on a base material.
  • the annual performance factor (APF) in an air conditioner is the efficiency of the air conditioner based on use status, and importance is placed on the efficiency at a load region lower than the rated point. For this reason, refrigerant compressors are often operated at low speed.
  • resin material such as PTFE which is an impregnated material is also used.
  • resin material has foreign substance adsorbing capabilities with which to adsorb wear particles (foreign substances) such as metal particles into the resin material, and thus has the effect of reducing seizure or wear due to wear particles.
  • wear particles foreign substances
  • metal particles (wear particles) adsorbed into the resin material may come into metal contact with the rotary shaft, resulting in seizure or galling.
  • FIG. 1 is a vertical cross section of a refrigerant compressor (scroll compressor) according to Embodiment 1 of the invention.
  • a sealed vessel 700 houses a compressor mechanism (located above), an electric motor 600 (located in the middle), and an oil sump 730 (located below).
  • the compressor mechanism and the electric motor 600 are connected to each other via a rotary shaft 300 formed of iron material.
  • the compressor mechanism includes two scrolls: a fixed scroll 100 having an end plate 101 and a vertically extending spiral wrap 102 and an orbiting scroll 200 having an end plate 201 and a vertically extending spiral wrap 202 .
  • the spiral warp 102 meshes with the spiral warp 202 , thereby forming the compressor mechanism.
  • the fixed scroll 100 also includes a gas inlet 103 and a gas outlet 104 .
  • the rotary shaft 300 is supported by a plain bearing (primary bearing) 401 and a secondary bearing 801 .
  • the plain bearing 401 lies within an upper frame 400 located above the electric motor 600 while the secondary bearing 801 lies within a lower frame 800 located below the electric motor 600 .
  • the upper frame 400 and the lower frame 800 are secured to the sealed vessel 700 .
  • An eccentric crank pin 301 formed of iron material is disposed at the upper end of the rotary shaft 300 and engages within a boss section 203 located below the end plate 201 of the orbiting scroll 200 .
  • Located within the boss section 203 is an orbiting plain bearing 210 within which the crack pin 301 slides.
  • An Oldham coupling 500 is also located at the back side of the end plate 201 of the orbing scroll 200 and allows the orbiting scroll 200 to orbit with respect to the fixed scroll 100 without rotating.
  • the crack pin 301 located at the upper end of the rotary shaft 300 is caused to rotate eccentrically. This in turn causes the orbiting scroll 200 to orbit with respect to the fixed scroll 100 .
  • the anti-rotating mechanism of the Oldham coupling 500 prevents the orbiting scroll 200 from rotating.
  • the orbital movement of the orbiting scroll 200 is followed by the introduction of gas into one of the successive enclosed spaces formed by spiral wraps 102 and 202 through an inlet pipe 711 and the gas inlet 103 .
  • the enclosed space containing the gas moves toward the scroll center and decreases in volume, thereby compressing the gas.
  • the compressed gas is discharged through the gas outlet 104 to an outlet chamber 710 .
  • the gas discharged into the outlet chamber 710 is then transferred around the compressor mechanism and the electric motor 600 and eventually discharged out of the scroll compressor through an outlet pipe 701 .
  • a bearing housing 802 designed to house the secondary bearing 801 , is attached to the lower frame 800 , and a pump 900 is disposed below the bearing housing 802 .
  • the pump 900 is driven via a pump joint 310 attached to the lower end of the rotary shaft 300 .
  • the pump 900 suctions oil from the oil sump 730 , followed by the transfer of the oil through the oil passageway 311 within the rotary shaft 300 up to the top section of the crack pin 301 .
  • the oil then lubricates the orbiting plain bearing 210 and flows along the plain bearing 401 . After lubricating the plain bearing 401 , the oil passes through an oil pipe 408 to return to the oil sump 730 .
  • part of the oil that has lubricated the orbiting plain bearing 210 passes the seal section 402 located between the bottom surface of the boss section 203 of the orbiting scroll and the upper frame 400 , flows to the back surface of the end plate 201 of the orbiting scroll, and from here, through an oil passageway 220 formed in the orbiting scroll end plate 201 , lubricates the slide sections between the fixed scroll 100 and the orbiting scroll 200 and lubricates between the wraps 102 and 202 , and is discharged into the outlet chamber 710 with the compressed gas. Thereafter, the oil discharged into the outlet chamber 710 returns to the oil sump 730 located at the bottom of the sealed vessel 700 .
  • FIG. 2 is an enlarged cross section of a section near the orbiting plain bearing 210 and the plain bearing (primary bearing) 401 shown in FIG. 1 where the components assigned the same reference numerals as those used in FIG. 1 represent the same components.
  • a lead-free resin-impregnated material is used for the plain bearings such as the orbiting plain bearing 210 and the plain bearing 401 , and at the same time, a hard film 1000 of a hardness of 1000 Hv or more (preferably 1500 Hv or more) is provided on the surface (outer surface) of the rotary shaft 300 that slides against the plain bearing (primary bearing) 401 and on the surface (outer surface) of the crack pin 301 that slides against the orbiting plain bearing 210 .
  • resin material having foreign substance adsorbing capabilities such as PTFE (polytetrafluoroethylene) is used.
  • resin material having foreign substance adsorbing capabilities POM (polyacetal), PBT (polybutylene terephthalate), PPS (polyphenylene sulfide), PEEK (polyether ether ketone), and or the like can also be used.
  • wear particles foreign substances
  • metal particles can be adsorbed into the resin material. Accordingly, seizure or wear of the plain bearings due to the wear particles can be reduced.
  • the hard film 1000 of a hardness of 1000 Hv or more (preferably 1500 Hv or more) is provided on the surface (outer surface) of the rotary shaft 300 that slides against the plain bearing 401 and on the surface (outer surface) of the crack pin 301 that slides against the orbiting plain bearing 210 , wear of the rotary shaft and the crank pin due to the wear particles and the occurrence of seizure or linear scars can be reduced significantly.
  • the hardness of the hard film is further increased, the effect on wear or linear scars of the rotary shaft is almost the same, but if the hardness is increased excessively, for example if a hard film of a hardness far greater than 3000 Hv, for example, of a hardness of 4000 Hv is used, due to the influence of the coarseness or irregularities of the surface of the rotary shaft or due to irregularities of the shaft surface resulting from peeling of the hard film, wear of the lead-free resin-impregnated bearings that slide against it is more likely to progress, which is not desirable.
  • FIG. 3 is a graph illustrating the relationship between the hardness of the hard film covering the rotary shaft and the bearing wear rates of the lead-free resin-impregnated bearings. This graph was confirmed by subjecting the refrigerant compressor (scroll compressor) to stress tests at the boundary lubrication region in which the oil film is difficult to form at low speed, and the horizontal axis represents the types of slid films covering rotary shafts (hardness of the hard films).
  • Non-coat (A) is a rotary shaft with no hard film whose hardness is about 600 Hv, and to form this rotary shaft, S45C was used as iron material, and its slide section was subjected to quenching treatment.
  • DLC (B) is an iron rotary shaft around which was applied a DLC (diamond-like carbon) film of a hardness of 3000 Hv
  • DLC (C) is an iron rotary shaft around which was applied a DLC film of a hardness of 4000 Hv.
  • the vertical axis represents the bearing wear rates (comparative wear rates) of lead-free resin-impregnated bearings having foreign substance adsorbing capabilities that slide against the rotary shafts DLC (B) and DLC (C) having other hard films.
  • a rotary shaft covered with a hard film of a hardness of 1000 Hv or more it is preferred to use a rotary shaft covered with a hard film of a hardness of 1000 Hv or more. Accordingly, in the present embodiment, by applying a hard film of a hardness range of 1000 Hv to 3000 Hv (preferably 1500 to 3000 Hv), the occurrence of seizure or galling in the bearing slide sections such as orbiting plain bearing 210 , the plain bearing 401 , the rotary shaft 300 , the crank pin 301 , and the like can be prevented. Since wear can also be prevented, a highly reliable refrigerant compressor capable of improving anti-wear properties can be obtained.
  • FIG. 4 is one showing a modification of FIG. 2 where the components assigned the same reference numerals as those used in FIG. 2 represent the same or corresponding components. While the example of FIG. 2 is one in which the layer of the hard film 1000 is directly formed by vapor deposition on the outer surface of the rotary shaft (the crank pin included) 300 , in the example shown in FIG. 4 , a hard film is provided by engaging a cylindrical member 302 formed of iron material covered with the hard film 1000 with the surfaces of the rotary shaft 300 and the crank pin 301 that slide against the orbiting plain bearing 210 and the plain bearing 401 .
  • a hard film of a hardness of 1000 Hv or more (preferably 1500 Hv or more) is formed in advance on the outer surface of the iron cylindrical member 302 by vapor deposition, the cylindrical member 302 is engaged with the locations of the rotary shaft 300 and the crank pin 301 that slide against the orbing plain bearing 210 and the plain bearing 410 .
  • productivity can be increased about five to ten times, and as a result, the costs of the refrigerant compressor can be reduced.
  • FIG. 5 is a diagram illustrating the structure of the base materials (the rotary shaft 300 and the cylindrical member 302 ) and the hard film 1000 shown in FIGS. 2 and 4 .
  • the component that acts as the base material on the surface of which a hard film is formed is the rotary shaft (including the crank pin) 300 shown in FIG. 2 or the cylindrical member 302 engaged with the rotary shaft as shown in FIG. 4 .
  • the hard film 1000 of a hardness of for example 1500 Hv is formed on the surfaces of these base materials.
  • a Cr-based film for example CrN
  • Ti-based film for example TiN
  • DLC film Si-DLC film or the like
  • These hard films 1000 can be formed on the base materials by vapor deposition, thereby forming the hard film on the surfaces of the base materials.
  • any of the aforementioned hard films has high corrosion resistance, is high in hardness, shows low friction coefficients, and is suitable as the sliding materials that slide against the plain bearings.
  • DLC diamond-like carbon
  • SP 3 bonds constituting diamond and SP 2 bonds having the graphite structure, and its hardness can be adjusted by adjusting coating conditions and varying bonding ratios.
  • each of the aforementioned hard films is capable of increasing surface smoothness, physical friction and wear are unlikely to occur, and a hard film of a hardness of 1500 Hv or more can be obtained with ease.
  • a refrigerant compressor capable of improving anti-wear properties can be obtained.
  • FIG. 6 is an enlarged cross section explaining another example in which a hard film is provided on the base materials, and the components assigned the same reference numerals as those used in FIG. 5 represent the same components.
  • the hardness of the iron material (base material) constituting the rotary shaft 300 is low, if a hard film of high hardness, for example, a DLC film of high hardness is formed, the hardness difference between the two is large, and while the refrigerant compressor is being operated, peeling of the hard film 1000 may occur due to deformation of the slide section.
  • the example of FIG. 6 is one explaining the method of forming a hard film on the base materials, which is effective in preventing peeling of the hard film 1000 .
  • This example is one in which between the hard film 1000 and the base materials (the rotary shaft 300 and the cylindrical 302 ), an intermediate layer 1001 having an intermediate hardness between the base materials and the hard film is provided.
  • the intermediate layer 1001 formed of a Cr-based film of a hardness of 1000 to 1500 Hv is formed on the base materials
  • the hard film 1000 formed of a DLC film of a hardness of 2000 to 3000 Hv is formed on the intermediate layer 1001 .
  • the intermediate layer 1001 can be formed by vapor deposition or the like.
  • FIG. 7 is an enlarged cross section explaining still another example in which a hard film is provided on the base materials, and the components assigned the same reference numerals as those used in FIG. 5 represent the same components.
  • the example of FIG. 7 is the same as the example of FIG. 5 in that the rotary shaft 300 and the cylindrical member 302 formed of iron material are used as the base materials and the hard film 1000 is formed on the base materials.
  • the example of FIG. 7 is distinctive in that the hard film 1000 is a tilted film whose hardness gradually increased from the base material side toward the slide surface side.
  • an Si-DLC film is used as the hard film 1000 , and this film is a tilted film whose Si amount (Si concentration) gradually decreased from the base material surface side toward the slide surface side.
  • the hardness of the hard film 1000 on the base material side is 1000 Hv or thereabout, and the hardness on the slide surface side is 1500 Hv or more.
  • the hard film formed of such a tilted film, too, can be formed on the surfaces of the base materials by vapor deposition.
  • the ion plating (IP) method As the method of not forming a complete boundary between the lower layer (base material side) and the upper layer (slide surface side) in the hard film 1000 and forming a tilted film that gradually changes from DLC to Si-DLC from the slide surface side to the base material side, the ion plating (IP) method, ion vapor deposition, and sputtering method are available. Other methods can also be employed as long as the desired hardness range can be achieved.
  • IP ion plating
  • ion vapor deposition ion vapor deposition
  • sputtering method Other methods can also be employed as long as the desired hardness range can be achieved.
  • the base materials (the rotary shaft 300 and the cylindrical member 302 ) are placed within a vacuum chamber of a vacuum degree of 10 3 to 10 ⁇ 5 Pa, and negative bias is applied to the materials. Meanwhile ionized materials for forming a hard film are electrically accelerated and caused to collide with the base materials, thereby forming a hard film on the surfaces of the base materials.
  • hydrocarbon-based gas such gas as C 6 H 6 or C 2 H 2
  • silane-based gas such as tetramethylsilane or the like
  • a Si-DLC film is first formed on the surfaces of the base materials according to the amount of the silane-based gas introduced. Thereafter, by reducing the amount of the silane-based gas gradually, a tilted film whose Si concentration gradually decreases from the base material side toward the slide surface side can be formed.
  • the Si-DLC film the higher the Si concentration, the lower the hardness, and the lower the Si concentration, the higher the hardness.
  • the hardness is set to the hardness close to the hardness of the base materials (for example, 1000 Hv), and the hardness can be made greater toward the slide surface side. At the slide surface, the hardness can be set to 2000 to 3000 Hv.
  • the Si amount of the hard film 1000 close to the base materials is preferred about 20 at. % in light of the adhesiveness with respect the base materials.
  • the plain bearings are formed by using lead-free resign-impregnated material having foreign substance adsorbing capabilities with which to adsorb wear particles, and the rotary shaft is formed of iron material. Also, a hard film of a hardness of 1000 Hv or more is provided at the section of the rotary shaft that slides against the plain bearings.
  • a highly reliable refrigerant compressor capable of preventing the occurrence of seizure or galling at the slide surface between the rotary shaft and the lead-free resin-impregnated bearings can be obtained.
  • wear particles can be adsorbed into the lead-free resin-impregnated material.
  • the occurrence of seizure or wear at the rotary shaft and the plain bearings can be reduced.
  • seizure or galling of the rotary shaft can be prevented, and good sliding capabilities can be ensured because the hard film harder and better in sliding capabilities than wear particles are provided on the rotary shaft surface.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Chemical & Material Sciences (AREA)
  • Ceramic Engineering (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
  • Compressor (AREA)
  • Rotary Pumps (AREA)
US13/815,000 2010-08-11 2011-08-08 Refrigerant Compressor Abandoned US20130195707A1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
JP2010180275A JP5385873B2 (ja) 2010-08-11 2010-08-11 冷媒圧縮機
JP2010-180275 2010-08-11
PCT/JP2011/068092 WO2012020740A1 (ja) 2010-08-11 2011-08-08 冷媒圧縮機

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US20130195707A1 true US20130195707A1 (en) 2013-08-01

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US13/815,000 Abandoned US20130195707A1 (en) 2010-08-11 2011-08-08 Refrigerant Compressor

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US (1) US20130195707A1 (ja)
JP (1) JP5385873B2 (ja)
CN (1) CN103069166B (ja)
WO (1) WO2012020740A1 (ja)

Cited By (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20140086775A1 (en) * 2012-09-24 2014-03-27 Jinsung Park Scroll compressor with bearing
EP2711553A3 (en) * 2012-09-24 2017-06-14 LG Electronics, Inc. Scroll compressor having a synthetic resin bearing
US11143442B2 (en) 2016-11-18 2021-10-12 Panasonic Intellectual Property Management Co., Ltd. Refrigerant compressor and freezer including same
US20210340967A1 (en) * 2018-11-08 2021-11-04 Panasonic Appliances Regrigeration Devices Singapore Refrigerant compressor and refrigeration apparatus using the same
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US11754072B2 (en) 2018-05-17 2023-09-12 Copeland Lp Compressor having capacity modulation assembly
US11846287B1 (en) 2022-08-11 2023-12-19 Copeland Lp Scroll compressor with center hub
US11965507B1 (en) 2022-12-15 2024-04-23 Copeland Lp Compressor and valve assembly
US12163523B1 (en) 2023-12-15 2024-12-10 Copeland Lp Compressor and valve assembly
US12173708B1 (en) 2023-12-07 2024-12-24 Copeland Lp Heat pump systems with capacity modulation
US12259163B2 (en) 2022-06-01 2025-03-25 Copeland Lp Climate-control system with thermal storage
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US20140086775A1 (en) * 2012-09-24 2014-03-27 Jinsung Park Scroll compressor with bearing
US9644629B2 (en) * 2012-09-24 2017-05-09 Lg Electronics Inc. Scroll compressor having a bearing lubricating layer
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US11143442B2 (en) 2016-11-18 2021-10-12 Panasonic Intellectual Property Management Co., Ltd. Refrigerant compressor and freezer including same
US11959670B2 (en) * 2016-11-18 2024-04-16 Panasonic Intellectual Property Management Co., Ltd. Refrigerant compressor and freezer including same
US20210389030A1 (en) * 2016-11-18 2021-12-16 Panasonic Intellectual Property Management Co., Ltd. Refrigerant compressor and freezer including same
US11261914B2 (en) * 2017-12-15 2022-03-01 Senju Metal Industry Co., Ltd. Sliding member and bearing
US11754072B2 (en) 2018-05-17 2023-09-12 Copeland Lp Compressor having capacity modulation assembly
US20210340967A1 (en) * 2018-11-08 2021-11-04 Panasonic Appliances Regrigeration Devices Singapore Refrigerant compressor and refrigeration apparatus using the same
US11655813B2 (en) 2021-07-29 2023-05-23 Emerson Climate Technologies, Inc. Compressor modulation system with multi-way valve
US11879460B2 (en) 2021-07-29 2024-01-23 Copeland Lp Compressor modulation system with multi-way valve
US12259163B2 (en) 2022-06-01 2025-03-25 Copeland Lp Climate-control system with thermal storage
US11846287B1 (en) 2022-08-11 2023-12-19 Copeland Lp Scroll compressor with center hub
US12188470B2 (en) 2022-08-11 2025-01-07 Copeland Lp Scroll compressor with center hub
US11965507B1 (en) 2022-12-15 2024-04-23 Copeland Lp Compressor and valve assembly
US12416308B2 (en) 2022-12-28 2025-09-16 Copeland Lp Compressor with shutdown assembly
US12173708B1 (en) 2023-12-07 2024-12-24 Copeland Lp Heat pump systems with capacity modulation
US12163523B1 (en) 2023-12-15 2024-12-10 Copeland Lp Compressor and valve assembly

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JP2012036878A (ja) 2012-02-23

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