WO2017094810A1 - Élément de glissement et compresseur du type à plateau oscillant - Google Patents

Élément de glissement et compresseur du type à plateau oscillant Download PDF

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Publication number
WO2017094810A1
WO2017094810A1 PCT/JP2016/085654 JP2016085654W WO2017094810A1 WO 2017094810 A1 WO2017094810 A1 WO 2017094810A1 JP 2016085654 W JP2016085654 W JP 2016085654W WO 2017094810 A1 WO2017094810 A1 WO 2017094810A1
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WO
WIPO (PCT)
Prior art keywords
coating layer
sliding member
solid lubricant
member according
swash plate
Prior art date
Application number
PCT/JP2016/085654
Other languages
English (en)
Japanese (ja)
Inventor
墾 窪田
翔悟 高木
Original Assignee
大豊工業株式会社
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
Priority claimed from JP2015235607A external-priority patent/JP6468991B2/ja
Priority claimed from JP2016167763A external-priority patent/JP2018035838A/ja
Application filed by 大豊工業株式会社 filed Critical 大豊工業株式会社
Publication of WO2017094810A1 publication Critical patent/WO2017094810A1/fr

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    • C—CHEMISTRY; METALLURGY
    • C10—PETROLEUM, GAS OR COKE INDUSTRIES; TECHNICAL GASES CONTAINING CARBON MONOXIDE; FUELS; LUBRICANTS; PEAT
    • C10M—LUBRICATING COMPOSITIONS; USE OF CHEMICAL SUBSTANCES EITHER ALONE OR AS LUBRICATING INGREDIENTS IN A LUBRICATING COMPOSITION
    • C10M169/00—Lubricating compositions characterised by containing as components a mixture of at least two types of ingredient selected from base-materials, thickeners or additives, covered by the preceding groups, each of these compounds being essential
    • C10M169/04—Mixtures of base-materials and additives
    • 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
    • F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
    • F04B27/08—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis
    • F04B27/10—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis having stationary cylinders
    • F04B27/12—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis having stationary cylinders having plural sets of cylinders or 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
    • 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
    • F16C33/10—Construction relative to lubrication
    • 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
    • C—CHEMISTRY; METALLURGY
    • C10—PETROLEUM, GAS OR COKE INDUSTRIES; TECHNICAL GASES CONTAINING CARBON MONOXIDE; FUELS; LUBRICANTS; PEAT
    • C10M—LUBRICATING COMPOSITIONS; USE OF CHEMICAL SUBSTANCES EITHER ALONE OR AS LUBRICATING INGREDIENTS IN A LUBRICATING COMPOSITION
    • C10M103/00—Lubricating compositions characterised by the base-material being an inorganic material
    • C—CHEMISTRY; METALLURGY
    • C10—PETROLEUM, GAS OR COKE INDUSTRIES; TECHNICAL GASES CONTAINING CARBON MONOXIDE; FUELS; LUBRICANTS; PEAT
    • C10M—LUBRICATING COMPOSITIONS; USE OF CHEMICAL SUBSTANCES EITHER ALONE OR AS LUBRICATING INGREDIENTS IN A LUBRICATING COMPOSITION
    • C10M103/00—Lubricating compositions characterised by the base-material being an inorganic material
    • C10M103/02—Carbon; Graphite
    • C—CHEMISTRY; METALLURGY
    • C10—PETROLEUM, GAS OR COKE INDUSTRIES; TECHNICAL GASES CONTAINING CARBON MONOXIDE; FUELS; LUBRICANTS; PEAT
    • C10M—LUBRICATING COMPOSITIONS; USE OF CHEMICAL SUBSTANCES EITHER ALONE OR AS LUBRICATING INGREDIENTS IN A LUBRICATING COMPOSITION
    • C10M103/00—Lubricating compositions characterised by the base-material being an inorganic material
    • C10M103/04—Metals; Alloys
    • C—CHEMISTRY; METALLURGY
    • C10—PETROLEUM, GAS OR COKE INDUSTRIES; TECHNICAL GASES CONTAINING CARBON MONOXIDE; FUELS; LUBRICANTS; PEAT
    • C10M—LUBRICATING COMPOSITIONS; USE OF CHEMICAL SUBSTANCES EITHER ALONE OR AS LUBRICATING INGREDIENTS IN A LUBRICATING COMPOSITION
    • C10M103/00—Lubricating compositions characterised by the base-material being an inorganic material
    • C10M103/06—Metal compounds
    • C—CHEMISTRY; METALLURGY
    • C10—PETROLEUM, GAS OR COKE INDUSTRIES; TECHNICAL GASES CONTAINING CARBON MONOXIDE; FUELS; LUBRICANTS; PEAT
    • C10M—LUBRICATING COMPOSITIONS; USE OF CHEMICAL SUBSTANCES EITHER ALONE OR AS LUBRICATING INGREDIENTS IN A LUBRICATING COMPOSITION
    • C10M107/00—Lubricating compositions characterised by the base-material being a macromolecular compound
    • C10M107/38—Lubricating compositions characterised by the base-material being a macromolecular compound containing halogen
    • C—CHEMISTRY; METALLURGY
    • C10—PETROLEUM, GAS OR COKE INDUSTRIES; TECHNICAL GASES CONTAINING CARBON MONOXIDE; FUELS; LUBRICANTS; PEAT
    • C10M—LUBRICATING COMPOSITIONS; USE OF CHEMICAL SUBSTANCES EITHER ALONE OR AS LUBRICATING INGREDIENTS IN A LUBRICATING COMPOSITION
    • C10M149/00—Lubricating compositions characterised by the additive being a macromolecular compound containing nitrogen
    • C10M149/12—Macromolecular compounds obtained otherwise than by reactions only involving carbon-to-carbon unsaturated bonds
    • C10M149/14—Macromolecular compounds obtained otherwise than by reactions only involving carbon-to-carbon unsaturated bonds a condensation reaction being involved
    • C10M149/18—Polyamides
    • 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
    • F16C17/00—Sliding-contact bearings for exclusively rotary movement
    • F16C17/04—Sliding-contact bearings for exclusively rotary movement for axial load only

Definitions

  • the present invention relates to a sliding member having a resin coating layer in which a solid lubricant is dispersed.
  • Patent Document 1 describes a sliding member provided with a plurality of recesses at the end of a sliding surface in order to prevent oil film destruction and seizure. The opening area of the recess increases as it goes to the end of the sliding surface.
  • Patent Document 1 the amount of solid lubricant on the sliding surface is not controlled, and there is room for improvement in oil retention.
  • the present invention provides a sliding member and a swash plate compressor with improved oil retention.
  • the present invention has a base material and a coating layer formed on the base material, and the coating layer has a binder resin and a solid lubricant dispersed in the binder resin, and the coating Provided is a sliding member having an exposure rate of 7% or more of the solid lubricant on the sliding surface of the layer.
  • the exposure rate of the solid lubricant on the sliding surface of the coating layer may be 10% or more.
  • the solid lubricant may have c-axis orientation, and the relative c-axis strength ratio of the solid lubricant in the coating layer may be 80% or more.
  • the occupation ratio of 50% of the depth from the surface roughness may be 50% or less with respect to the maximum surface roughness.
  • the occupation rate may be 70% or less.
  • the surface roughness of the sliding surface of the coating layer may be 1 to 20 ⁇ m.
  • the surface roughness may be 8 to 15 ⁇ m.
  • the base material may have a swash plate shape used in a swash plate compressor.
  • the base material may have a thrust surface that receives a thrust load.
  • the thrust surface may have a taper / land structure or a step / land structure formed by the coating layer.
  • the base material has a semi-ring shape
  • the thrust surface has a relief at a circumferential end of the semi-ring
  • the coating layer may not be formed on the relief.
  • the thrust surface has an oil groove, and the coating layer may not be formed in the oil groove.
  • the present invention provides a swash plate compressor using any one of the above sliding members as a swash plate.
  • oil retention and initial conformability can be improved in a sliding member and a swash plate compressor.
  • FIG. 3 is a schematic view illustrating the structure of a coating layer 32.
  • FIG. 3 is a schematic diagram showing an orientation state of a solid lubricant 322 in a coating layer 32.
  • FIG. 5 is a schematic diagram showing an outline of a load curve of the coating layer 32.
  • 6 is a flowchart illustrating a method for manufacturing the swash plate 3.
  • the figure which illustrates the structure of the thrust washer 10 concerning another embodiment.
  • FIG. 1 is a schematic cross-sectional view illustrating a structure of a compressor 1 according to an embodiment.
  • the compressor 1 is a so-called swash plate compressor.
  • the compressor 1 has a shaft 2, a swash plate 3, a piston 4, and a shoe 5.
  • the shaft 2 is rotatably supported with respect to a housing (not shown).
  • the swash plate 3 is fixed obliquely with respect to the rotation axis of the shaft 2.
  • the swash plate 3 is an example of the sliding member of the present invention.
  • the piston 4 reciprocates in a cylinder bore (not shown) provided in the housing.
  • the shoe 5 is provided between the swash plate 3 and the piston 4, and slides with the swash plate 3 and the piston 4, respectively.
  • the surface that slides with the swash plate 3 is substantially flat, and the surface that slides with the piston 4 has a dome-like (hemispherical) shape.
  • the rotation of the shaft 2 is converted into a reciprocating motion of the piston 4 by the swash plate 3.
  • FIG. 2 is a diagram illustrating the structure of the swash plate 3.
  • FIG. 2 is a schematic diagram showing a structure in a cross section perpendicular to the sliding surface with the shoe 5.
  • the swash plate 3 has a base material 31, a coating layer 32, and a coating layer 33. Both the coating layer 32 and the coating layer 33 slide with the shoe 5.
  • the base material 31 has a disk shape, and is formed of a metal that satisfies required characteristics, for example, an iron-based, copper-based, or aluminum-based alloy. From the viewpoint of preventing adhesion with the shoe 5, the swash plate 3 is preferably formed of a material different from that of the shoe 5.
  • FIG. 3 is a schematic view illustrating the structure of the coating layer 32.
  • the coating layer 32 is provided to improve the characteristics of the sliding surface of the swash plate 3.
  • the coating layer 32 has a binder resin 321 and a solid lubricant 322.
  • the coating layer 32 includes, for example, 20 to 70 vol% solid lubricant.
  • the balance is a binder resin.
  • the binder resin 321 is formed of, for example, a thermosetting resin.
  • As the thermosetting resin for example, at least one of polyamideimide (PAI), polyamide (PA), polyimide (PI), epoxy, polyetheretherketone, phenol, and elastomer is used.
  • Solid lubricant 322 is added to improve lubrication characteristics.
  • Examples of the solid lubricant 322 include crystalline substances having c-axis orientation, such as MoS 2 , graphite (Gr), carbon, fluororesin, soft metals (Sn, Bi, etc.), WS 2 , and h-BN. At least one is used.
  • a crystalline substance having c-axis orientation refers to a substance having a layered crystal structure, such as a hexagonal system.
  • the coating layer 32 may include other additives such as hard particles in addition to the solid lubricant 322. As the hard particles, for example, at least one of oxide, nitride, carbide, and sulfide is used.
  • the thickness of the coating layer 32 is preferably 10 ⁇ m or more, more preferably 15 ⁇ m or more, and further preferably 20 ⁇ m or more.
  • the thickness of the coating layer 32 is less than 5 ⁇ m, the coating layer 32 may be worn and the substrate 31 may be exposed. When the base material 31 is exposed, there arises a problem that the coefficient of friction increases or adheres to the shoe 5. Further, if the coating layer 32 is too thick, the seizure resistance may be lowered. Therefore, the thickness is preferably 50 ⁇ m or less.
  • the relative c-axis strength ratio of the solid lubricant 322 in the coating layer 32 is preferably 80% or more, and more preferably 85% or more.
  • the relative c-axis intensity ratio refers to the ratio of the diffraction peak intensity from the cleavage plane to the total diffraction peak intensity in X-ray diffraction. More specifically, the relative c-axis intensity ratio is determined from the (002), (004), (100), (101), (102), (103), (105), (110), and (008) planes.
  • Is defined as the ratio of the integrated value of diffraction peak intensities from the (002), (004), and (008) planes to the integrated value of diffraction peak intensities. Although diffraction peaks from other than the above nine crystal planes may appear, they are ignored in calculating the relative c-axis intensity ratio because the peak intensity is weak.
  • the state in which the relative c-axis intensity ratio is 80% or more, that is, the state in which the relative c-axis intensity ratio is high means that the crystal orientation of the solid lubricant 322 is aligned in the coating layer 32.
  • the relative c-axis intensity ratio is hereinafter referred to as “orientation ratio” in the sense that it indicates the degree of alignment of crystal orientations.
  • orientation ratio in the sense that it indicates the degree of alignment of crystal orientations.
  • solid lubricants exhibit a low coefficient of friction due to interlayer slip in crystals having a layer structure.
  • the fact that the crystal orientations are aligned means that the directions in which interlayer slip occurs are aligned.
  • FIG. 4 is a schematic diagram showing the orientation state of the solid lubricant 322 in the coating layer 32.
  • FIG. 4A shows a state where the orientation rate is low
  • FIG. 4B shows a state where the orientation rate is high.
  • the solid lubricant 322 is represented as hexagonal flakes.
  • the solid lubricant 322 has a cleaved surface aligned in a direction substantially parallel to the sliding surface.
  • the average particle diameter of the solid lubricant 322 is, for example, 1 to 10 ⁇ m.
  • the average particle diameter is measured by, for example, a laser diffraction method.
  • FIG. 5 is a schematic diagram showing an outline of the load curve of the coating layer 32.
  • the load curve represents the load length ratio of the contour curve element expressed as a function of the cutting level.
  • the load curve is defined in JIS B0601: 2013.
  • the cutting level refers to the depth from the maximum peak height of the contour curve for obtaining a cutting surface parallel to the surface of the base material of the sliding surface.
  • the maximum peak height is the cutting level 0%
  • the maximum valley depth is the cutting level 100%.
  • the load length ratio Rmr (c) represents a ratio of the load length Ml (c) of the contour curve element at the cutting level c to the evaluation length (the following formula (1)). Note that ln represents the evaluation length, and m represents the number of peaks at the cutting level c.
  • the load length ratio Rmr at the position where the cutting level c is 50% is preferably 70% or less, and more preferably 50% or less.
  • the relatively small load length ratio means that even if the surface of the coating layer is worn by several ⁇ m due to initial conformance, the recess still remains, and the lubricant can be retained in this recess, so that the conformability and lubrication can be maintained. Excellent characteristics.
  • the recesses are not discontinuous like the recesses of Patent Document 1, and are continuous with each other. Therefore, a flow is generated in the lubricating oil. As a result, cooling of the sliding heat generation proceeds and the sliding characteristics are not impaired.
  • the coating layer 33 is formed in the same manner as the coating layer 32.
  • FIG. 11 is a diagram illustrating the structure of a thrust washer 10 according to another embodiment.
  • the thrust washer 10 is a crank washer used together with a main bearing in an engine such as an automobile, for example, and is another example of the sliding member according to the present invention.
  • the crank washer has a function of supporting a thrust force applied to the crankshaft (not shown) and positioning the cylinder block (not shown) and the crankshaft in the axial direction.
  • the main bearing and the thrust washer 10 are accommodated in the cylinder block and the cap. Both the cylinder block and the cap are examples of a housing.
  • the thrust washer 10 has a semi-ring shape.
  • the semi-annular shape refers to a shape obtained by cutting a circle having a circular hole in the center in almost half when viewed from a viewpoint away from the thrust washer in the axial direction of the shaft indicated by the bearing.
  • the direction along the circumference of the half ring is referred to as the circumferential direction
  • the direction from the center of the ring (circle) toward the outside is referred to as the radial direction.
  • the thrust washer 10 has a thrust surface 11, a mating surface 12, and a mating surface 13.
  • the thrust surface 11 is a surface that receives a thrust force. In FIG. 1, the thrust surface 11 faces the front.
  • the length perpendicular to the circumferential direction on the thrust surface 11 is referred to as the width of the thrust washer 10.
  • the mating surface 12 and the mating surface 13 are surfaces facing other thrust washers when two semi-circular thrust washers are used in combination.
  • the thrust washer 10 further has an oil groove 14 and an oil groove 15.
  • the oil groove 14 and the oil groove 15 have a function of holding lubricating oil and supplying the held lubricating oil to the thrust surface.
  • the thrust washer 10 has an outer diameter of 20 to 40 mm and a thickness of 1 to 4 mm.
  • the inner diameter of the thrust washer 10 is designed according to the size of the bearing used together, but is preferably 2.5 times or more the thickness of the thrust washer 10.
  • the width of the bottom of the oil groove is 2 to 7 mm, and the depth is 0.2 to 0.5 mm.
  • FIG. 12 is a diagram illustrating a cross-sectional structure of the thrust washer 10.
  • FIG. 2 shows a virtual cross-sectional view in which the thrust washer 10 is cut along the circumferential direction at the center in the width direction and developed in a plane.
  • the thrust washer 10 has a substrate 21 and a coating layer 22.
  • the base material 21 is formed of a material that satisfies required mechanical characteristics and sliding characteristics, for example, an iron-based, copper-based, or aluminum-based alloy. From the viewpoint of preventing adhesion between the housing and the crankshaft, the base material 21 is preferably formed of a material different from that of the housing and the crankshaft.
  • the coating layer 22 is formed on at least a part of a surface corresponding to the thrust surface 11 (hereinafter referred to as a surface 211) of the base material 21.
  • the coating layer 22 is provided in order to improve the characteristics of the thrust surface 11.
  • the surface 211 is substantially flat, and the taper / land structure is formed on the thrust surface 11 by the coating layer 22.
  • the taper / land structure refers to a surface structure having a taper portion 23 and a land portion 24.
  • the land portion refers to a portion whose surface height is higher than other portions.
  • the surface height refers to a length (distance) from a predetermined reference surface (for example, the surface 211) on the substrate 21 to the surface of the coating layer 22.
  • the taper portion is a portion where the height gradually decreases from the land portion.
  • the taper / land structure is formed along the circumferential direction, and in the cross section along the radial direction, the heights of the taper portion 23 and the land portion 24 are both constant.
  • the thrust surface 11 When the thrust surface 11 receives a thrust force, or when the thrust surface 11 slides with the mating member, an oil film pressure due to the wedge effect is generated in the taper / land structure. Further, in this example, the land portions 24 are formed on both sides of the tapered portion 23, and the oil film pressure is more effectively formed as compared with the example in which the land portion 24 is formed only on one side of the tapered portion 23. Can do.
  • the coating layer 22 is not formed on the portion of the surface 211 where the oil groove 14 and the oil groove 15 are formed, and the base material 21 is exposed.
  • the coating layer 22 is not formed on the portion of the surface 211 where the oil groove 14 and the oil groove 15 are formed, and the base material 21 is exposed.
  • the taper / land structure illustrated in FIG. 12 is formed, for example, by applying two or more times by pad printing.
  • the material of the coating layer 22 is the same as that of the coating layer 32.
  • the surface structure of the thrust surface 11 is not limited to that exemplified in the embodiment.
  • FIG. 2 shows an example in which the tapered portions 23 are provided on both sides of the land portion 24 in the circumferential cross section.
  • the taper portion 23 may be provided only on one side of the land portion 24.
  • the thrust surface 11 may have a step / land structure instead of the taper / land structure.
  • the step / land structure refers to a surface structure having a step portion and a land portion. The land portion is as described in the taper / land structure.
  • the step portion refers to a portion whose height is discretely lowered from the land portion.
  • the step / land structure is formed along the circumferential direction, and the height of each of the step portion and the land portion is constant in the cross section along the radial direction.
  • the thrust surface 11 receives a thrust force, or when the thrust surface 11 slides with the counterpart material, an oil film pressure due to the wedge effect is generated in the step / land structure.
  • the thrust surface 11 does not have a surface structure such as a taper / land structure or a step / land structure, and may be flat in portions other than the oil groove 14 and the oil groove 15.
  • FIG. 13 is a diagram showing another example of the structure of the thrust washer 10.
  • FIG. 13 schematically shows a cross-sectional view of the thrust washer 10 cut along a cross section perpendicular to the axial direction.
  • the thrust washer 10 has a thrust relief 16 on the thrust surface 11.
  • the thrust relief 16 is a relief for preventing local contact that occurs in the vicinity of the mating surface when the seating surfaces of the two housings (for example, the cylinder block and the cap) used in combination are displaced in the axial direction.
  • the coating layer 22 is not formed, and the base material 21 is exposed.
  • the thrust washer 10 may have a structure other than that illustrated in FIGS. 11 and 12.
  • the thrust washer 10 may have at least one of a mating surface relief, a detent, and a detent relief.
  • the mating surface relief is a relief for preventing local contact of a crankshaft (not shown) in the vicinity of the mating surface, and means a structure in which the inner diameter of the crank washer is wide in the vicinity of the mating surface.
  • the rotation stopper is a structure for preventing the thrust washer 10 from rotating with respect to the housing.
  • the detent is, for example, a protrusion formed on the outer periphery in the radial direction.
  • the anti-rotation relief is a relief for preventing local contact with the housing in the vicinity of the anti-rotation.
  • the shape, position, and number of oil grooves on the thrust surface 11 are not limited to those illustrated in FIGS.
  • the oil groove 14 and the oil groove 15 are formed in a direction extending radially from the center of the half ring of the thrust washer 10.
  • the oil groove may be formed to extend in a direction perpendicular to the mating surface.
  • the number of oil grooves is not limited to two, and may be one or three or more. Alternatively, the oil groove may be omitted.
  • FIG. 6 is a flowchart illustrating a manufacturing method of the sliding member.
  • a substrate is prepared.
  • the base material is molded into a predetermined shape.
  • the base material is molded into a disk shape.
  • the base material is molded into a disk shape.
  • the thrust washer 10 is manufactured, the base material is formed in a semi-annular shape.
  • the base material is formed, for example, by cutting (cutting) or punching.
  • the surface of the substrate may be roughened.
  • a paint for forming a coating layer is prepared.
  • the binder resin and the solid lubricant are mixed by a known method. These mixtures are diluted with a diluent. Any diluent may be used. For example, N-methylpyrrolidone (NMP) is used. The blending ratio of the diluent is, for example, 30 to 70% by volume with respect to the solid content.
  • NMP N-methylpyrrolidone
  • the blending ratio of the diluent is, for example, 30 to 70% by volume with respect to the solid content.
  • step S4 paint is applied to the surface of the substrate.
  • the paint is applied, for example, by pad printing, roll coating, or spray coating. When the thickness of the paint that can be applied at one time is limited, two or more overcoats may be performed.
  • step S5 the coating layer is dried and baked.
  • the surface roughness (Rzjis in JIS B 0601: 2001) of the coating layer is, for example, preferably 1 to 20 ⁇ m, and more preferably 8 to 15 ⁇ m. After application of the paint, drying and baking are performed (step S5).
  • Experimental Example Test pieces of sliding members were prepared under various conditions, and their characteristics were evaluated. More specifically, a plurality of test pieces were produced in each of the four sections of Experimental Examples 1 to 4.
  • the material and composition of the coating layer 32 are common.
  • PAI was used as the binder resin
  • MoS 2 and graphite were used as the solid lubricant.
  • 40 vol% of the solid lubricant was added to 60 vol% of the binder resin.
  • graphite was 10 vol% and MoS 2 was 30 vol%.
  • only MoS 2 was added as a solid lubricant without using graphite.
  • the average particle size of MoS 2 was about 2 ⁇ m, and the average particle size of graphite was 5 to 10 ⁇ m.
  • cast iron (FCD700) was used as the substrate.
  • Table 1 shows the measurement results of the orientation ratio and the surface roughness in Experimental Examples 1 to 4.
  • Samples coated with pad printing (Experimental Examples 1 and 4) and other methods (Experimental Example 2: roll coating, Experimental Example 3: spray coating) are compared, and the sample coated with pad printing is oriented. A high tendency was seen.
  • a thin film is laminated to obtain a desired film thickness.
  • the film thickness per layer is about the same as the size of the additive, the effect of pressing the additive is obtained, and a high orientation ratio is obtained.
  • roll coating and spray coating a film having a desired thickness is applied once. Therefore, when the additive size is used as a reference, the film thickness becomes thicker (than the pad coat), the effect of pressing the additive becomes weak, and a relatively low orientation rate can be obtained.
  • the solid lubricant is not simply dependent on the coating method. It is considered that this also depends on the particle size of the particles.
  • FIG. 7 is a graph showing the solid lubricant exposure rate in Experimental Examples 1 to 3.
  • the solid lubricant exposure rate was calculated by the following procedure. First, a photomicrograph of the coating layer surface is taken. An area of MoS 2 is specified by using image processing software from the color shading in the photographed micrograph. The area ratio of the MoS 2 region with respect to the observation region is calculated and used as the solid lubricant exposure rate. As is clear from this measurement procedure, the solid lubricant exposure rate here is the exposure rate of MoS 2 .
  • the solid lubricant exposure rates were 7.9%, 12.3%, and 7.7%.
  • the solid lubricant exposure rates were 1.3%, 0.8%, and 0.5%.
  • the solid lubricant exposure rates were 8.1%, 9.2%, and 13.0%.
  • the solid lubricant falls off the surface and the solid lubricant exposure rate is low. Conceivable.
  • a solid lubricant exposure rate of 15% was obtained.
  • FIG. 8 is a diagram showing the dependency of the coefficient of friction on the amount of MoS 2 added. This figure shows how the friction coefficient changes when the amount of MoS 2 added to the coating layer is changed when the coating layer is formed by roll coating as in Experimental Example 2. From this figure, it can be seen that the friction coefficient tends to decrease as the amount of MoS 2 added to the entire coating layer increases. From this result, it is predicted that the friction coefficient decreases as the exposure amount of MoS 2 on the sliding surface increases.
  • FIG. 9 is a schematic diagram showing load curves of Experimental Example 1 and Experimental Example 2.
  • 8A shows the load curve of Experimental Example 1
  • FIG. 10 is a graph showing the dependency of the contact angle of the lubricating oil on the load length ratio Rmr (50).
  • the sliding member according to the present invention is not limited to the one used as the swash plate 3 of the compressor 1 or the crank washer.
  • the sliding member according to the present invention may be used as a sliding member other than a swash plate compressor or a crank washer, such as a half bearing or a bush.
  • the material, composition, film thickness, etc. of the coating layer in the experimental example are merely examples. The present invention is not limited to this.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Chemical & Material Sciences (AREA)
  • Chemical Kinetics & Catalysis (AREA)
  • General Chemical & Material Sciences (AREA)
  • Oil, Petroleum & Natural Gas (AREA)
  • Organic Chemistry (AREA)
  • Sliding-Contact Bearings (AREA)

Abstract

L'invention concerne un plateau oscillant (3) qui est un élément de glissement, lequel plateau oscillant (3) comprenant une base (31) et une couche de revêtement (32) formée sur la base (31). La couche de revêtement (32) comprend une résine servant de liant (321) et un lubrifiant solide (322) dispersé dans la résine servant de liant (321). Dans la couche de revêtement (32), le degré d'exposition du lubrifiant solide (322) sur la surface de glissement est de 7 % ou plus.
PCT/JP2016/085654 2015-12-02 2016-12-01 Élément de glissement et compresseur du type à plateau oscillant WO2017094810A1 (fr)

Applications Claiming Priority (4)

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JP2015235607A JP6468991B2 (ja) 2015-12-02 2015-12-02 摺動部材および斜板式コンプレッサ
JP2015-235607 2015-12-02
JP2016167763A JP2018035838A (ja) 2016-08-30 2016-08-30 スラストワッシャ
JP2016-167763 2016-08-30

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Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2020097948A (ja) * 2018-12-17 2020-06-25 大豊工業株式会社 摺動部材

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS601384A (ja) * 1983-06-17 1985-01-07 Taiho Kogyo Co Ltd 斜板式コンプレツサ−
JPH05157115A (ja) * 1991-02-09 1993-06-22 Taiho Kogyo Co Ltd 摺動材料
JP2003138367A (ja) * 2001-10-29 2003-05-14 Sulzer Metco (Japan) Ltd 溶射皮膜、溶射皮膜の形成方法及び溶射原料粉末
JP2005133593A (ja) * 2003-10-29 2005-05-26 Taiho Kogyo Co Ltd 斜板式コンプレッサの斜板
JP2007255311A (ja) * 2006-03-23 2007-10-04 Daido Metal Co Ltd 摺動部材及びその製造方法
JP2012026414A (ja) * 2010-07-28 2012-02-09 Taiho Kogyo Co Ltd 斜板式コンプレッサ
WO2012074107A1 (fr) * 2010-12-02 2012-06-07 大豊工業株式会社 Plateau oscillant pour compresseur à plateau oscillant

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS601384A (ja) * 1983-06-17 1985-01-07 Taiho Kogyo Co Ltd 斜板式コンプレツサ−
JPH05157115A (ja) * 1991-02-09 1993-06-22 Taiho Kogyo Co Ltd 摺動材料
JP2003138367A (ja) * 2001-10-29 2003-05-14 Sulzer Metco (Japan) Ltd 溶射皮膜、溶射皮膜の形成方法及び溶射原料粉末
JP2005133593A (ja) * 2003-10-29 2005-05-26 Taiho Kogyo Co Ltd 斜板式コンプレッサの斜板
JP2007255311A (ja) * 2006-03-23 2007-10-04 Daido Metal Co Ltd 摺動部材及びその製造方法
JP2012026414A (ja) * 2010-07-28 2012-02-09 Taiho Kogyo Co Ltd 斜板式コンプレッサ
WO2012074107A1 (fr) * 2010-12-02 2012-06-07 大豊工業株式会社 Plateau oscillant pour compresseur à plateau oscillant

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2020097948A (ja) * 2018-12-17 2020-06-25 大豊工業株式会社 摺動部材
WO2020129318A1 (fr) * 2018-12-17 2020-06-25 大豊工業株式会社 Élément coulissant
JP7171409B2 (ja) 2018-12-17 2022-11-15 大豊工業株式会社 摺動部材

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