WO2013175623A1 - Machine rotative et dispositif à cycle de réfrigération - Google Patents

Machine rotative et dispositif à cycle de réfrigération Download PDF

Info

Publication number
WO2013175623A1
WO2013175623A1 PCT/JP2012/063473 JP2012063473W WO2013175623A1 WO 2013175623 A1 WO2013175623 A1 WO 2013175623A1 JP 2012063473 W JP2012063473 W JP 2012063473W WO 2013175623 A1 WO2013175623 A1 WO 2013175623A1
Authority
WO
WIPO (PCT)
Prior art keywords
bearing
bush
crankshaft
peripheral surface
bearing part
Prior art date
Application number
PCT/JP2012/063473
Other languages
English (en)
Japanese (ja)
Inventor
小山田　具永
Original Assignee
株式会社日立製作所
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 株式会社日立製作所 filed Critical 株式会社日立製作所
Priority to PCT/JP2012/063473 priority Critical patent/WO2013175623A1/fr
Priority to JP2014516599A priority patent/JP5963854B2/ja
Publication of WO2013175623A1 publication Critical patent/WO2013175623A1/fr

Links

Images

Classifications

    • 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
    • F16C33/06—Sliding surface mainly made of metal
    • F16C33/12—Structural composition; Use of special materials or surface treatments, e.g. for rust-proofing
    • F16C33/121—Use of special materials
    • 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
    • F04B39/0238—Hermetic compressors with oil distribution channels
    • F04B39/0246—Hermetic compressors with oil distribution channels in the rotating shaft
    • 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
    • F04C29/0057—Means for transmitting movement from the prime mover to driven parts of the pump, e.g. clutches, couplings, transmissions for eccentric movement
    • 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
    • F16C33/24—Brasses; Bushes; Linings with different areas of the sliding surface consisting of different materials
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B1/00—Compression machines, plants or systems with non-reversible cycle
    • F25B1/04—Compression machines, plants or systems with non-reversible cycle with compressor of rotary type
    • 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
    • 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
    • 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
    • F04C2240/56—Bearing bushings or details thereof
    • 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
    • F04C2240/60—Shafts
    • F04C2240/605—Shaft sleeves or details thereof
    • 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
    • F05C2251/00—Material properties
    • F05C2251/04—Thermal properties
    • F05C2251/042—Expansivity
    • F05C2251/046—Expansivity dissimilar
    • 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
    • F05C2251/14—Self lubricating materials; Solid lubricants
    • 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
    • F16C2202/00—Solid materials defined by their properties
    • F16C2202/20—Thermal properties
    • F16C2202/22—Coefficient of expansion
    • 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
    • F16C2360/00—Engines or pumps
    • F16C2360/42—Pumps with cylinders or pistons
    • 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
    • F16C2360/00—Engines or pumps
    • F16C2360/44—Centrifugal pumps

Definitions

  • the present invention relates to a rotary machine and a refrigeration cycle apparatus, and more particularly, to a rotary machine including a sliding bearing portion that slides on an outer peripheral surface of a rotating shaft via a lubricating oil, and a refrigeration cycle apparatus.
  • a scroll compressor as a rotating machine is a compressor that compresses a gas such as a refrigerant by relatively rotating two scroll members having a spiral tooth shape.
  • the other movable orbiting scroll is configured to orbit with respect to the fixed scroll restrained by screw fastening or welding.
  • the orbiting scroll is provided with an orbiting slide bearing that engages and slides with the eccentric part of the crankshaft. Then, while the eccentric portion of the crankshaft and the orbiting slide bearing slide through the lubricating oil, the swinging rotational motion of the eccentric portion of the crankshaft is transmitted to the orbiting scroll, and the orbiting scroll is caused to orbit.
  • a crankshaft that is connected to the rotor of the electric motor and rotates is supported by sliding through a lubricant with respect to a journal slide bearing called a main bearing and a sub-bearing fixed in the scroll compressor.
  • Patent Document 1 As a conventional technique for reducing the bearing loss, there is a technique described in Japanese Patent Laid-Open No. 2003-239876 (Patent Document 1). According to Patent Document 1, “a floating ring member 110 is held in an insertion groove 8 a of a hub 8 formed in a lower part of the orbiting scroll 5 so as to be capable of rotating and idling. The slide bush 10 fixed to the eccentric part 4a is inserted to constitute a friction loss reducing device of the scroll compressor "(see summary).
  • Patent Document 1 In general, it is known that in a sliding part such as a bearing that slides on two surfaces via lubricating oil, bearing loss due to oil film shear increases as the sliding speed increases.
  • the technique described in Patent Document 1 has a structure in which a self-rotating floating ring member is disposed in a space between a slide bush and a hub fixed to an eccentric portion of a rotating shaft filled with lubricating oil. .
  • the sliding that occurs between the slide bush fixed to the eccentric portion of the rotating shaft and the hub, the sliding between the outer periphery of the slide bush and the inner periphery of the floating ring member, and the outer periphery of the floating ring member and the hub It is possible to disperse and slide between the circumferences. For this reason, the relative sliding speed in each sliding part becomes small, and the bearing loss by oil film shearing is reduced.
  • Patent Document 2 states that “the bearing has a main bearing 6c that supports the main shaft portion 7a and a crank bearing 4c that supports the crank portion 7b.
  • the main bearing 6c includes the crank side main bearing 6c1 and the crank side.
  • the crank bearing 4c and the crank side main bearing 6c1 are constituted by carbon bearings in which pores of a carbonaceous base material containing graphite are impregnated with metal, which are adjacent to the main bearing.
  • the bearing 6c2 is composed of a wound bush formed by winding a plate material "(see abstract).
  • crank bearing and the crank side main bearing which are high load portions with high surface pressure, are constituted by carbon bearings, so that reliability such as wear resistance and seizure resistance in a boundary lubrication state is achieved. Is secured.
  • Patent Document 3 “at least one of the slewing bearing, the main bearing, and the sub-bearing has an oil-impregnated porous body in a surface in sliding contact with the crankshaft. It is described as “a scroll compressor” characterized in that a surface other than the surface in sliding contact with the shaft is surrounded by a member that does not penetrate oil (see claim 1). Further, “at least one of the slewing bearing, the main bearing, and the sub-bearing is an elastic body in which both ends of the surface slidingly contacting the crankshaft do not permeate oil, and the surfaces other than the both ends are oil-containing porous. The surface of the oil-containing porous body other than the surface in sliding contact with the crankshaft is surrounded by the elastic body or a member that does not penetrate oil ”(see claim 6).
  • the performance of the bearing is improved, and in an environment where the lubrication state is severe, such as when oil is out, a piece hit, a non-steady state such as refrigerant foaming, or when using alternative CFCs with poor lubricity.
  • the odor can also ensure compression performance and reliability.
  • Patent Document 3 promotes the inflow of lubricating oil from the oil-containing porous body into the gap between the shaft and the bearing when oil film formation becomes difficult, and prevents direct contact between the shaft and the bearing. This is effective in reducing bearing loss.
  • the bearing loss is not reduced or very limited.
  • the object of the present invention is to reduce the bearing loss during fluid lubrication and reduce the bearing loss during fluid lubrication by reducing the shear resistance of the oil film due to the lubricating oil existing between the outer peripheral surface of the rotating shaft and the sliding bearing. It is another object of the present invention to provide a rotating machine and a refrigeration cycle apparatus that can maintain reliability as a bearing.
  • a rotating machine reflecting one aspect of the present invention includes a rotating shaft, a housing portion having a hole into which the shaft is inserted, and an axial direction of the housing portion in the hole.
  • a sliding bearing having an intermediate bearing portion larger than two bearing portions and sliding with respect to the outer peripheral surface of the shaft via lubricating oil.
  • a refrigeration cycle apparatus reflecting one aspect of the present invention is characterized in that the rotary machine is provided as a refrigerant compressor for refrigeration or air conditioning.
  • the present invention by reducing the shear resistance of the oil film due to the lubricating oil existing between the outer peripheral surface of the rotating shaft and the slide bearing, it is possible to reduce bearing loss during fluid lubrication, It is possible to provide a rotating machine and a refrigeration cycle apparatus that can maintain reliability as a bearing even during a load operation.
  • FIG. 2 is an enlarged cross-sectional view of the vicinity of a main bearing when the scroll compressor shown in FIG. 1 is operating at a high load. It is a graph which shows the relationship between the expansion ratio of the clearance gap between an intermediate
  • FIG. 1 is a longitudinal sectional view showing a scroll compressor 100 according to the first embodiment of the present invention. That is, in this 1st Embodiment, the rotary machine of this invention is demonstrated using the example of the scroll compressor 100 which compresses refrigerant
  • the scroll compressor 100 is a hermetic compressor used for refrigerating and air conditioning such as an air conditioner such as an air conditioner or a refrigerating apparatus.
  • the scroll compressor 100 includes a sealed container 102 that forms a casing, and a fixed scroll 103 and a turning scroll 104 that orbits and engages with the fixed scroll 103 are provided in an upper portion of the sealed container 102. ing.
  • the fixed scroll 103 and the orbiting scroll 104 each have a spiral tooth shape portion.
  • an electric motor 105 as a rotational power source is provided in the sealed container 102, and a crankshaft (shaft) 106 is connected to the rotor of the electric motor 105.
  • a crankshaft 106 that is connected to the electric motor 105 and rotates is provided by a main bearing (slide bearing) 108 provided on a frame 107 fixed in the sealed container 102 and a sub-bearing 110 provided on a lower frame 109. It is supported rotatably.
  • An eccentric portion 106 a having an eccentricity with respect to the axial center of the portion supported by the main bearing 108 and the auxiliary bearing 110 of the crankshaft 106 is provided on the upper portion of the crankshaft 106.
  • the eccentric portion 106a slides by engaging with the orbiting bearing 112 provided on the lower surface (rear surface) side of the end plate 104a of the orbiting scroll 104, so that the swinging rotational motion (eccentric motion) of the eccentric portion 106a is the orbiting scroll. 104.
  • the rotation of the orbiting scroll 104 is restricted by the Oldham ring 113, and the orbiting scroll 104 orbits with respect to the fixed scroll 103.
  • the Oldham ring 113 is attached to a groove formed on the lower surface (back surface) side of the end plate 104 a of the orbiting scroll 104 and a groove formed on the frame 107.
  • an oil supply hole 116 penetrating from the lower end to the end face (upper end face) side of the eccentric portion 106a is provided along the axial direction.
  • Lubricating oil 117 stored in the lower part of the sealed container 102 is supplied to the oil supply hole by a pressure difference described later using the discharge pressure of the refrigerant gas or by a pump (not shown) separately attached to the lower end of the crankshaft 106. It is configured to be pushed up through 116 and supplied to a gap between the inner peripheral surface of each bearing (main bearing 108, sub-bearing 110, slewing bearing 112) and the outer peripheral surface of the crankshaft 106.
  • the inside of the sealed container 102 is at a discharge pressure
  • an intermediate chamber (back pressure chamber) 118 formed on the lower surface side of the end plate 104a of the orbiting scroll 104 is an intermediate pressure between the discharge pressure and the suction pressure. It has become.
  • the lubricating oil 117 stored in the lower portion of the sealed container 102 is supplied to the bearings 108, 110, 112, and the like through the oil supply holes 116 due to a pressure difference between the discharge pressure and the intermediate pressure.
  • FIG. 2 is an enlarged cross-sectional view of the vicinity of the main bearing 208 in a scroll compressor as a comparative example.
  • the main bearing 208 according to the comparative example includes two cylindrical sliding bearing bushes in a through hole 107 b formed inside a bearing housing 107 a provided in a part of the frame 107.
  • the upper bush 120 and the lower bush 122 are arranged side by side in the axial direction.
  • the upper bush 120 is disposed on the side closer to the eccentric part 106a
  • the lower bush 122 is disposed on the side far from the eccentric part 106a.
  • Lubricating oil is supplied to the gap between the outer peripheral surface of the crankshaft 106 and the inner peripheral surface of the main bearing 208 (the upper bush 120 and the lower bush 122) through the oil supply hole 116 and the oil supply port 119. And the inner peripheral surface of the main bearing 208 slide through an oil film. The lubricating oil that has formed the oil film then flows out of the bearing housing 107a through the end of the bearing housing 107a.
  • FIG. 3 is an enlarged cross-sectional view of the vicinity of the main bearing 108 in the scroll compressor 100 according to the first embodiment of the present invention.
  • the main bearing 108 according to the first embodiment includes a through hole (hole) 107b formed inside a bearing housing (housing portion) 107a provided in a part of a frame 107 made of cast iron, for example.
  • the upper bush (first bearing portion) 120, the intermediate bush (intermediate bearing portion) 121, and the lower bush (second bearing portion) 122, which are three cylindrical plain bearing bushes, are arranged in the order from above. It has a structure arranged side by side.
  • the upper bush 120 is disposed closest to one end (on the eccentric portion 106a side) in the axial direction in the through hole 107b, that is, on the side closest to the eccentric portion 106a.
  • the lower bush 122 is disposed closest to the other end (on the opposite side to the eccentric portion 106a) in the axial direction in the through hole 107b, that is, on the side farthest from the eccentric portion 106a.
  • the intermediate bush 121 is disposed between the upper bush 120 and the lower bush 122.
  • the upper bush 120 and the lower bush 122 are made of, for example, a carbon bearing material in which a carbonaceous substrate containing graphite is impregnated with a metal.
  • the intermediate bush 121 includes a carbon bearing material that forms the upper bush 120 and the lower bush 122 and a material that exhibits a higher linear expansion coefficient than the cast iron material that forms the bearing housing 107a, such as a resin. Consists of materials.
  • the gap between the intermediate bush 121 and the outer peripheral surface of the crankshaft 106 is the gap between the upper bush 120 and the outer peripheral surface of the crankshaft 106, and the lower bush 122.
  • the clearance between the outer peripheral surface of the crankshaft 106 is larger. That is, the difference between the inner diameter of the intermediate bush 121 and the outer diameter of the crankshaft 106 is larger than the difference between the inner diameter of the upper bush 120 and the outer diameter of the crankshaft 106, and the inner diameter of the lower bush 122 and the crankshaft 106. It is larger than the difference with the outer diameter.
  • An oil supply hole 116 is formed in a gap (hereinafter also referred to as “bearing gap”) between the outer peripheral surface of the crankshaft 106 and the inner peripheral surface of the main bearing 108 (the upper bush 120, the intermediate bush 121, and the lower bush 122).
  • the lubricating oil is supplied through the oil supply port 119, and the outer peripheral surface of the crankshaft 106 and the inner peripheral surface of the main bearing 108 slide through an oil film.
  • the lubricating oil that has formed the oil film then flows out of the bearing housing 107a through the end of the bearing housing 107a.
  • F is the oil film shear force
  • ⁇ is the oil film shear stress
  • ⁇ is the absolute viscosity
  • V is the peripheral speed of the rotating shaft
  • h is the radial gap (oil film thickness)
  • A is the area of the inner circumference of the bearing related to the oil film shear. is there.
  • the total area of the inner peripheral surfaces of all the sliding bearing bushes is equal, and the inner diameters of the upper bush 120 and the lower bush 122 are the same.
  • the radial gap h is set to be larger than that of the comparative example in the intermediate bush 121 portion, the oil film shear force and consequently the bearing loss is reduced as compared with the comparative example.
  • the material, thickness, and inner diameter of the upper bush 120, the intermediate bush 121, and the lower bush 122, which are sliding bearing bushes, and the bearing housing 107a are determined according to the operating conditions and operating temperature of the scroll compressor 100. By doing so, it is possible to secure a load (load capacity) that can be supported by the main bearing 108 at the time of high-load operation equivalent to the conventional one, and to maintain the reliability as the bearing.
  • FIG. 4 is an enlarged cross-sectional view of the vicinity of the main bearing 108 when the scroll compressor 100 shown in FIG. 1 is operating at a high load.
  • FIG. 4 shows a state where the crankshaft 106 is slightly inclined with respect to the main bearing 108 during high load operation (the same applies to FIGS. 9 and 10). The reason why the crankshaft 106 is inclined will be described later.
  • the linear expansion coefficient of the intermediate bush 121 is particularly large, the clearance between the intermediate bush 121 and the crankshaft 106 is lower during high load operation (see FIG. 4). It becomes smaller than during operation (see FIG. 3). Therefore, in the state at the time of high load operation, the region in which a high oil film pressure can be maintained by the dynamic pressure is expanded compared to the state at the time of low load operation.
  • the gas load 123 acts on the crankshaft 106 as an overhanging load at a position above the main bearing 108, so that the inclination of the crankshaft 106 with respect to the main bearing 108 is an operating load. It is easy to expand with the increase. For this reason, direct contact between the crankshaft 106 and the main bearing 108 tends to occur at the bearing end portions indicated by A and B in FIG. In the example shown in FIG. 3, since the upper bush 120 and the lower bush 122 are made of a hard and lubricating carbon bearing material, it is difficult to form an oil film, and the crankshaft 106 and the main bearing 108 are directly connected to each other. Even when it is in a state of sliding with contact, good wear resistance can be obtained.
  • the bearing loss due to oil film shearing when the crankshaft 106 was slid through the lubricating oil was evaluated.
  • the influence of the gap between the intermediate bush 121 and the crankshaft 106 on the bearing loss and the minimum oil film thickness in the bearing structure according to the first embodiment of the present invention was verified. The verification results are shown in FIGS.
  • crankshaft 106 had a diameter of 14 to 18 mm in the scroll compressor 100 for an air conditioner. Further, the upper bush 120, the intermediate bush 121, and the lower bush 122 have the same axial length and the same diameter as the crankshaft 106. The clearances between the upper bush 120 and the lower bush 122 and the crankshaft 106 were equally 0.15% of the diameter of the crankshaft 106. The inclination angle of the crankshaft 106 with respect to the main bearing 108 was set to 0.01 ° in the acting load direction.
  • FIG. 5 is a graph showing the result of evaluating the bearing loss by changing the enlargement ratio of the gap between the intermediate bush 121 and the crankshaft 106 in various ways. That is, FIG. 5 shows the relationship between the expansion ratio of the gap between the intermediate bush and the crankshaft and the relative bearing loss.
  • the horizontal axis indicates an increase in the gap between the intermediate bush 121 and the crankshaft 106 when the gap between the upper bush 120 and the lower bush 122 and the crankshaft 106 is set as a reference (0%). Indicates the rate.
  • the vertical axis shows the relative value when the bearing loss is 100% when the gaps between the upper bush 120, the intermediate bush 121, and the lower bush 122 and the crankshaft 106 are all equal. Yes.
  • the bearing loss tended to decrease by increasing the gap between the intermediate bush 121 and the crankshaft 106.
  • FIG. 6 is a graph showing the result of evaluating the minimum oil film thickness by variously changing the enlargement ratio of the gap between the intermediate bush 121 and the crankshaft 106. That is, FIG. 6 shows the relationship between the expansion ratio of the gap between the intermediate bush and the crankshaft and the relative minimum oil film thickness.
  • the horizontal axis indicates an increase in the gap between the intermediate bush 121 and the crankshaft 106 when the gap between the upper bush 120 and the lower bush 122 and the crankshaft 106 is set as a reference (0%). Indicates the rate.
  • the vertical axis represents the relative value when the minimum oil film thickness is 100% when the gaps between the upper bush 120, the intermediate bush 121, and the lower bush 122 are all equal to the crankshaft 106. Show.
  • the minimum oil film thickness is the minimum oil film thickness when the same load is supported. As shown in the verification result of FIG. 6, the minimum oil film thickness tended to increase by reducing the gap between the intermediate bush 121 and the crankshaft 106.
  • the scroll compressor 100 includes the crankshaft 106 that rotates and the bearing housing 107a having the through-hole 107b into which the crankshaft 106 is inserted, and the through-hole of the bearing housing 107a. And a main bearing 108 that is disposed in the hole 107b and slides on the outer peripheral surface of the crankshaft 106 via lubricating oil.
  • the main bearing 108 has an upper bush 120 disposed closest to one end in the axial direction in the through hole 107b of the bearing housing 107a, a lower bush 122 disposed closest to the other end, and the upper bush 120. And an intermediate bush 121 disposed between the lower bush 122 and the lower bush 122.
  • the intermediate bush 121 has a linear expansion coefficient larger than that of the bearing housing 107a, the upper bush 120, and the lower bush 122, and at least a gap between the outer periphery of the crankshaft 106 before the crankshaft 106 starts rotating. Is larger than the upper bush 120 and the lower bush 122.
  • the intermediate bush 121 arranged at the center is provided at both ends. It is made of a material having a linear expansion coefficient larger than that of the upper bush 120 and the lower bush 122, and at least between the crankshaft 106 and the upper bush 120 and the lower bush 122 before the crankshaft 106 starts rotating. The gap between is large. This gap relationship is maintained in the same way even during high-temperature operation (where the bearing temperature is high) and during low-temperature operation where the rotational speed and working load of the crankshaft 106 are small (the bearing temperature is low). Be drunk. Then, the inner diameter dimensional change rate (reduction rate) of the intermediate bush 121 due to the temperature change becomes larger than the inner diameter dimensional change rate (reduction rate) of the upper bush 120 and the lower bush 122.
  • the gap between the intermediate bush 121 and the crankshaft 106 is large, so that friction loss is reduced and bearing loss is reduced. To do. Further, since the gaps at the upper bush 120 and the lower bush 122, which are the outflow paths of the lubricating oil, are small, the increase in the flow rate of the lubricating oil hardly occurs, and an increase in loss due to this is prevented.
  • the bearing by reducing the shear resistance of the oil film caused by the lubricating oil existing between the outer peripheral surface of the rotating crankshaft 106 and the main bearing 108, the bearing at the time of fluid lubrication. Loss can be reduced, and reliability as a bearing can be maintained even during high load operation.
  • a carbon-based, metal-based, or ceramic-based material having a linear expansion coefficient smaller than that of the intermediate bush 121 can be used.
  • a carbon bearing material in which a metal is impregnated with a carbonaceous base material containing graphite is used with emphasis on ensuring wear resistance at the time of one-piece contact and direct contact friction due to oil film breakage.
  • materials of the upper bush 120 and the lower bush 122 for example, cast iron, carbon steel, copper alloy, brass, tin alloy, aluminum alloy according to the wear resistance and environment resistance required for the rotating machine to be applied. Zirconia, alumina, silicon carbide, silicon nitride, etc. may be used.
  • the material of the intermediate bush 121 As the material of the intermediate bush 121, a resin material having a larger linear expansion rate than the material of the upper bush 120 and the lower bush 122 can be used. However, as the material of the intermediate bush 121, polytetrafluoroethylene, polyether ether ketone, polyphenylene sulfide, nylon, polyimide, polyamideimide, polyethylene, depending on the temperature conditions of the rotating machine to be applied and the expected change in bearing clearance Ultra high molecular weight polyethylene and the like, and composite materials of these resins and sintered metals, particles, fiber materials, and the like may be used.
  • FIG. 7 is an enlarged cross-sectional view of the vicinity of the main bearing 108a according to the first modification of the first embodiment.
  • the detailed description of the configuration and operation similar to those of the first embodiment shown in FIGS. 1 to 6 will be omitted as they are incorporated in the first modification, and different points will be described (further described below). The same applies to the modified example).
  • the first modification of the first embodiment is different from the first embodiment in that the lower bush 122a of the main bearing 108a is formed integrally with the bearing housing 107a.
  • the upper bushing may be formed integrally with the bearing housing 107a instead of the lower bushing 122a. That is, instead of installing the upper bush 120 and the lower bush 122 as separate members in the bearing housing 107a as in the first embodiment, the lower bush 122a (or the upper bush) is integrated with the bearing housing 107a.
  • FIG. 8 is an enlarged cross-sectional view of the vicinity of the main bearing 108b according to the second modification of the first embodiment.
  • the outer diameter of the crankshaft 106 is smaller than the other portions in the portion of the main bearing 108b that faces the intermediate bush 121a. That is, the method of enlarging the bearing gap at the center of the main bearing 108b is to increase the outer diameter of the crankshaft 106 at the portion facing the intermediate bush 121a instead of increasing the inner diameter of the intermediate bush 121 as in the first embodiment. It is also possible to make it smaller.
  • the coaxiality of the inner peripheral surfaces of the upper bush 120, the intermediate bush 121, and the lower bush 122, which are three plain bearing bushes, is obtained with high accuracy.
  • the three slide bearing bushes are inserted into the bearing housing 107a and heated to the temperature during the high load operation of the scroll compressor 100. It is necessary to devise a processing process such as processing the inner diameter of each plain bearing bush to the same diameter.
  • the inner diameters of the upper bush 120, the intermediate bush 121a, and the lower bush 122, which are three plain bearing bushes are set to be equal at room temperature. The same diameter can be processed by one axial feed. According to such a second modification of the first embodiment, it is possible to reduce the manufacturing cost in addition to the same effects as the first embodiment described above.
  • FIG. 9 is an enlarged cross-sectional view of the vicinity of the main bearing 108c according to a third modification of the first embodiment.
  • the third modification of the first embodiment at least one groove 124 that divides the inner peripheral surface in the circumferential direction is formed on the inner peripheral surface of the intermediate bush 121b.
  • the intermediate bush 121b in addition to being able to achieve the same operational effects as those of the first embodiment described above, by providing the groove 124, the intermediate bush 121b can be In addition to relieving the internal stress in the circumferential direction and reducing variations in the inner diameter change due to temperature rise, the sliding area is reduced by the amount of the groove 124, so that the bearing loss can be further reduced.
  • FIG. 10 is an enlarged cross-sectional view of the vicinity of the main bearing 108d according to a fourth modification of the first embodiment.
  • a groove 124a that divides the inner peripheral surface in the circumferential direction is formed on the inner peripheral surface of the intermediate bush 121c.
  • the intermediate bush 121c has a V-shape extending from both end portions in the axial direction toward the central portion so as to incline in the rotational direction of the crankshaft 106.
  • the lubricating oil passes through the groove 124a and is drawn from both ends in the axial direction of the intermediate bush 121c to the central portion, and the pressure near the central portion increases. For this reason, it is possible to increase the minimum oil film thickness by improving the dynamic pressure especially at high load.
  • FIG. 11 is a longitudinal sectional view showing a rotary compressor 130 according to the second embodiment of the present invention. That is, in this 2nd Embodiment, the rotary machine of this invention is demonstrated using the example of the rotary compressor 130 which compresses refrigerant gas.
  • the rotary compressor 130 functionally includes a vertical cylindrical sealed container 138, a compression mechanism 139 that compresses refrigerant gas in the sealed container 138, and an electric motor that drives the compression mechanism 139. 131 and an oil sump 144 for storing lubricating oil to be supplied to the sliding surfaces of the components and members constituting the compression mechanism 139.
  • an electric motor 131, a compression mechanism 139, and an oil sump 144 are arranged in order from the top.
  • a rotating shaft (shaft) 132 extending downward is connected to the rotor of the electric motor 131.
  • the compression mechanism 139 includes an eccentric shaft portion 132a formed near the lower tip portion of the rotary shaft 132, and a cylindrical roller 133 that is eccentrically rotated by the eccentric shaft portion 132a when the eccentric shaft portion 132a is engaged inside.
  • a cylinder 134 that houses the eccentric shaft portion 132a and the roller 133, an upper bearing member 135 that serves as an upper lid of the cylinder 134 and supports the rotating shaft 132, and a lower lid of the cylinder 134 and supports the lower end portion of the rotating shaft 132.
  • a vane (not shown) that slides on the outer peripheral surface of the roller 133 and separates the low pressure side and the high pressure side of the compression chamber 137 from each other.
  • the upper bearing member 135 has a bearing housing (housing portion) 135 a provided in a part of the upper bearing member 135.
  • a through hole (hole) 135b into which the rotary shaft 132 is inserted is formed in the bearing housing 135a, and an upper bearing (slide bearing) 143 is disposed in the through hole 135b.
  • the upper bearing 143 includes an upper bush (first bearing portion) 140 and an intermediate bush (intermediate bearing portion) 141 that are three cylindrical slide bearing bushes in a through hole 135b formed inside the bearing housing 135a.
  • the lower bush (second bearing portion) 142 is arranged in the axial direction in order from above.
  • the upper bushing 140 is disposed closest to one end (the side opposite to the eccentric shaft portion 132a) in the axial direction in the through hole 135b, that is, on the side farthest from the eccentric shaft portion 132a.
  • the lower bush 142 is disposed closest to the other end (on the eccentric shaft portion 132a side) in the axial direction in the through hole 135b, that is, on the side closest to the eccentric shaft portion 132a.
  • the intermediate bush 141 is disposed between the upper bush 140 and the lower bush 142.
  • the material of the upper bush 140 and the lower bush 142 is, for example, cast iron.
  • the lower bushing 142 (including the sliding surface that is the inner peripheral surface thereof) is formed integrally with the bearing housing 135a of the upper bearing member 135.
  • the intermediate bush 141 is made of a material whose linear expansion coefficient is larger than the linear expansion coefficients of the upper bush 140 and the lower bush 142 and larger than the linear expansion coefficient of the bearing housing 135a, for example, a material containing resin. Has been.
  • the gap between the intermediate bush 141 and the outer peripheral surface of the rotary shaft 132 is the gap between the upper bush 140 and the outer peripheral surface of the rotary shaft 132 and the lower bush 142.
  • the clearance between the outer peripheral surface of the rotary shaft 132 and the outer peripheral surface of the rotary shaft 132 is larger.
  • the outer diameter of the rotating shaft 132 is smaller in the portion facing the intermediate bush 141 of the upper bearing 143 than in the other portions.
  • the difference between the inner diameter of the intermediate bush 141 and the outer diameter of the rotating shaft 132 at the portion facing the intermediate bush 141 is larger than the difference between the inner diameter of the upper bush 140 and the outer diameter of the rotating shaft 132, and It is larger than the difference between the inner diameter of the bush 142 and the outer diameter of the rotating shaft 132.
  • a lower bearing 145 (including a sliding surface that is an inner peripheral surface) that is a slide bearing that supports the lower end portion of the rotating shaft 132 is formed integrally with a lower bearing member 136 made of cast iron.
  • Lubricating oil 117 in an oil sump 144 provided at the lower portion of the rotary compressor 130 passes through an oil supply hole 146 formed along the axial center of the rotary shaft 132 through a branch hole in the radial direction, and the upper bearing 143 and the lower bearing.
  • 145, and a sliding portion of each of the bearings 143 and 145 is formed with an oil film by lubricating oil to ensure smooth lubrication.
  • the gap between the intermediate bush 141 and the rotary shaft 132 is large. Is reduced and bearing loss is reduced. Further, since the gap in the upper bush 140 and the lower bush 142, which is the lubricating oil outflow path, is small, the flow rate of the lubricating oil hardly increases and an increase in loss due to this is prevented.
  • the bearing at the time of fluid lubrication Loss can be reduced, and reliability as a bearing can be maintained even during high load operation.
  • the bearings 143 and 145 are provided at positions close to the compression chamber 137.
  • the lower bush 142 and the lower bearing 145 located at the end of the upper bearing member 135 on the roller 133 side function as sliding bearing bushes, and the sliding surfaces that are the inner peripheral surfaces thereof are bearing members 135 and 136. And are integrally formed. This eliminates fluid movement in portions other than the bearing gap, such as the inside of the material of the sliding bearing bush, as in the case where the sliding bearing bush is configured separately from the bearing members 135 and 136. Therefore, it is easy to control the inflow / outflow relationship of gas and lubricating oil between the bearings 143 and 145 and the compression chamber 137, and the design becomes easy.
  • the upper bush, the intermediate bush, and the lower bush which are three plain bearing bushes, are arranged in the axial direction in order from above in a through hole formed inside the bearing housing. It has a structure.
  • the present invention is not limited to this, and can be applied to a structure in which four or more plain bearing bushes are arranged side by side in the axial direction.
  • the sliding bearing bushes at both ends in the axial direction correspond to the upper bushing and the lower bushing in the embodiment, and at least of the plurality of sliding bearing bushes disposed between the sliding bearing bushes at both axial ends.
  • One corresponds to the intermediate bush in the embodiment.
  • a method of reducing the outer diameter of the crankshaft 106 at a portion facing the intermediate bush 121a is adopted as a method of expanding the bearing gap at the center portion of the main bearing 108b.
  • the present invention is not limited to this.
  • the inner diameter of the intermediate bush 121 may be enlarged, and the outer diameter of the crankshaft 106 at the portion facing the intermediate bush 121a may be reduced.
  • segments the said internal peripheral surface into the circumferential direction was formed in the internal peripheral surface of the intermediate bush 121b
  • this invention is based on this. It is not limited. The present invention is also applicable to the case where the depth of the groove 124 reaches the outer peripheral surface of the intermediate bush 121b, for example.
  • the intermediate bush 121b may be configured to be divided into a plurality of portions in the circumferential direction by a dividing surface along the axial direction, and to include a plurality of portions forming a part of a cylindrical shape.
  • the present invention is not limited to these and can be applied to other types of compressors. is there.
  • the said embodiment demonstrated the vertical compressor with which the axis
  • the present invention can also be applied to a horizontal compressor arranged along.
  • the present invention can also be applied to various types of rotating machines that include a sliding bearing portion that slides on the outer peripheral surface of a rotating shaft via a lubricating oil.
  • the present invention can be configured as a refrigeration cycle device including the rotating machine according to the present invention as a refrigerant compressor for refrigeration or air conditioning.
  • This refrigeration cycle equipment includes a refrigerant compressor as a rotating machine according to the present invention, a condenser that dissipates heat from refrigerant gas that has been compressed by the refrigerant compressor into a high temperature and high pressure, and decompresses the high-pressure refrigerant from the condenser. And a evaporator for evaporating the liquid refrigerant from the pressure reducing device.
  • a refrigeration cycle apparatus can be used for a refrigeration apparatus, an air conditioner, a heat pump type hot water heater, and the like.

Abstract

L'invention porte sur une machine rotative, qui comporte : un vilebrequin (106) ; un logement de palier (107a) qui a un trou traversant (107b) ; et un palier principal (108) qui est disposé à l'intérieur du trou traversant (107b) et qui coulisse par rapport à la surface périphérique externe du vilebrequin (106), une huile de lubrification étant entre ceux-ci. Le palier principal (108) a un coussinet supérieur (120), un coussinet inférieur (122) et un coussinet intermédiaire (121) qui est disposé entre le coussinet supérieur (120) et le coussinet inférieur (122). Le coussinet intermédiaire (121) a un coefficient de dilatation linéaire supérieur à celui du logement de palier (107a), du coussinet supérieur (120) et du coussinet inférieur (122), et, avant le début de la rotation d'au moins le vilebrequin (106), l'espace entre le coussinet intermédiaire (121) et la surface périphérique externe du vilebrequin (106) est supérieur à l'espace entre le coussinet intermédiaire (121) et le coussinet supérieur (120) et à l'espace entre le coussinet intermédiaire (121) et le coussinet inférieur (122). En résultat de cette configuration, une perte de palier pendant une lubrification de fluide peut être réduite, et la fiabilité en tant que palier peut être conservée même pendant un fonctionnement à charge élevée.
PCT/JP2012/063473 2012-05-25 2012-05-25 Machine rotative et dispositif à cycle de réfrigération WO2013175623A1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
PCT/JP2012/063473 WO2013175623A1 (fr) 2012-05-25 2012-05-25 Machine rotative et dispositif à cycle de réfrigération
JP2014516599A JP5963854B2 (ja) 2012-05-25 2012-05-25 回転機械および冷凍サイクル機器

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/JP2012/063473 WO2013175623A1 (fr) 2012-05-25 2012-05-25 Machine rotative et dispositif à cycle de réfrigération

Publications (1)

Publication Number Publication Date
WO2013175623A1 true WO2013175623A1 (fr) 2013-11-28

Family

ID=49623352

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/JP2012/063473 WO2013175623A1 (fr) 2012-05-25 2012-05-25 Machine rotative et dispositif à cycle de réfrigération

Country Status (2)

Country Link
JP (1) JP5963854B2 (fr)
WO (1) WO2013175623A1 (fr)

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN104455000A (zh) * 2014-12-24 2015-03-25 赵长江 一种石墨干粉润滑轴承及其加工工艺
CN113236565A (zh) * 2021-05-06 2021-08-10 珠海格力节能环保制冷技术研究中心有限公司 轴系结构及涡旋压缩机
CN115199530A (zh) * 2022-06-17 2022-10-18 安徽凯特泵业有限公司 恒温输送泵的泵体衬套总成
WO2022264792A1 (fr) * 2021-06-18 2022-12-22 パナソニックＩｐマネジメント株式会社 Compresseur à spirale
US11655819B2 (en) * 2018-08-13 2023-05-23 Mitsubishi Heavy Industries Thermal Systems, Ltd. Scroll compressor

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH0419421A (ja) * 1989-12-12 1992-01-23 Nippon Seiko Kk 動圧みぞ付軸受及びその製造方法
JPH04160224A (ja) * 1990-10-22 1992-06-03 Nippon Seiko Kk すべり軸受
JPH0571540A (ja) * 1991-09-13 1993-03-23 Nippon Seiko Kk すべり軸受
JPH08281748A (ja) * 1995-04-11 1996-10-29 Japan Steel Works Ltd:The 射出成形機のトグル機構用の軸受装置
JP2003294028A (ja) * 2002-04-01 2003-10-15 Torishima Pump Mfg Co Ltd 水中軸受

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH0419421A (ja) * 1989-12-12 1992-01-23 Nippon Seiko Kk 動圧みぞ付軸受及びその製造方法
JPH04160224A (ja) * 1990-10-22 1992-06-03 Nippon Seiko Kk すべり軸受
JPH0571540A (ja) * 1991-09-13 1993-03-23 Nippon Seiko Kk すべり軸受
JPH08281748A (ja) * 1995-04-11 1996-10-29 Japan Steel Works Ltd:The 射出成形機のトグル機構用の軸受装置
JP2003294028A (ja) * 2002-04-01 2003-10-15 Torishima Pump Mfg Co Ltd 水中軸受

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN104455000A (zh) * 2014-12-24 2015-03-25 赵长江 一种石墨干粉润滑轴承及其加工工艺
US11655819B2 (en) * 2018-08-13 2023-05-23 Mitsubishi Heavy Industries Thermal Systems, Ltd. Scroll compressor
CN113236565A (zh) * 2021-05-06 2021-08-10 珠海格力节能环保制冷技术研究中心有限公司 轴系结构及涡旋压缩机
WO2022264792A1 (fr) * 2021-06-18 2022-12-22 パナソニックＩｐマネジメント株式会社 Compresseur à spirale
CN115199530A (zh) * 2022-06-17 2022-10-18 安徽凯特泵业有限公司 恒温输送泵的泵体衬套总成

Also Published As

Publication number Publication date
JPWO2013175623A1 (ja) 2016-01-12
JP5963854B2 (ja) 2016-08-03

Similar Documents

Publication Publication Date Title
JP5963854B2 (ja) 回転機械および冷凍サイクル機器
WO2014064919A1 (fr) Compresseur rotatif
EP2700818B1 (fr) Compresseur à volutes
JP2005201140A (ja) 流体機械
TW201447107A (zh) 冷媒壓縮機
WO2015025416A1 (fr) Machine rotative, et appareil à cycle de réfrigération
JP2001065458A (ja) 圧縮機
US9115715B2 (en) Compressor with pressure reduction groove formed in eccentric part
JP2001115959A (ja) 圧縮機
JP3823325B2 (ja) 冷凍機用圧縮機の軸受および冷凍機用圧縮機
JP2002147354A (ja) 圧縮機
JP2015161209A (ja) 圧縮機及び冷凍サイクル機器
JP4325611B2 (ja) 冷凍機用圧縮機の軸受および冷凍機用圧縮機
JP6184648B1 (ja) 軸受ユニット及び圧縮機
JP5091019B2 (ja) スクロール膨張機
JP5640885B2 (ja) スクロール型圧縮機
JP2005325842A (ja) 流体機械
JP6618663B1 (ja) すべり軸受構造及びスクロール圧縮機
JP7010202B2 (ja) 流体機械
WO2016143186A1 (fr) Compresseur comprenant un palier lisse
JP6104396B2 (ja) スクロール圧縮機
JP2020193626A (ja) 冷凍機用圧縮機の軸受
JP5864883B2 (ja) スクロール圧縮機
JP2002147377A (ja) スクロール圧縮機およびジャーナル軸受部の製造方法
JP2005133586A (ja) 密閉型冷媒圧縮機

Legal Events

Date Code Title Description
121 Ep: the epo has been informed by wipo that ep was designated in this application

Ref document number: 12877430

Country of ref document: EP

Kind code of ref document: A1

ENP Entry into the national phase

Ref document number: 2014516599

Country of ref document: JP

Kind code of ref document: A

NENP Non-entry into the national phase

Ref country code: DE

122 Ep: pct application non-entry in european phase

Ref document number: 12877430

Country of ref document: EP

Kind code of ref document: A1