WO2013005394A1 - Sliding member - Google Patents
Sliding member Download PDFInfo
- Publication number
- WO2013005394A1 WO2013005394A1 PCT/JP2012/004161 JP2012004161W WO2013005394A1 WO 2013005394 A1 WO2013005394 A1 WO 2013005394A1 JP 2012004161 W JP2012004161 W JP 2012004161W WO 2013005394 A1 WO2013005394 A1 WO 2013005394A1
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- WO
- WIPO (PCT)
- Prior art keywords
- sliding
- sliding member
- recess
- region
- area
- Prior art date
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Classifications
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- 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
- F04C29/02—Lubrication; Lubricant separation
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
-
- 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
-
- 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
- F16C33/06—Sliding surface mainly made of metal
- F16C33/10—Construction relative to lubrication
- F16C33/1025—Construction relative to lubrication with liquid, e.g. oil, as lubricant
- F16C33/103—Construction relative to lubrication with liquid, e.g. oil, as lubricant retained in or near the bearing
-
- 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
- F04B2201/00—Pump parameters
- F04B2201/12—Parameters of driving or driven means
- F04B2201/1207—Wear of the bearings
-
- 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
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- 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
- F04C18/0246—Details concerning the involute wraps or their base, e.g. geometry
-
- 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
- F04C2230/92—Surface treatment
-
- 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
- F16C2362/00—Apparatus for lighting or heating
- F16C2362/52—Compressors of refrigerators, e.g. air-conditioners
Definitions
- the present invention relates to the surface shape of a sliding member, and in particular to a sliding surface of a sliding member mainly made of a metal material with respect to an apparatus in a compressor for a refrigeration cycle and the like.
- the thickness of the oil film existing between the sliding members is about 1 to 2 ⁇ m or less at the commonly used rotation speed of 1500 to 3000 rpm .
- a technique of processing for forming a recess on the sliding surface of the smoothed sliding member there has been proposed a technique of processing for forming a recess on the sliding surface of the smoothed sliding member. Specifically, a technique has been proposed in which an infinite number of concave portions having a substantially arc-shaped cross section are formed on the sliding surface of the sliding member (see, for example, Patent Document 1).
- FIG. 10 and FIG. 11 show a state in which the sliding members sliding relative to each other are opposed via an oil film (not shown) of lubricating oil.
- FIG. 10 shows a state in which the sliding surfaces of the sliding member 30 facing the sliding member 32 are both smoothed.
- FIG. 11 shows that the sliding surface of the opposing sliding member 30 is made smooth and the sliding surface 38 of the other sliding member 32 is provided with innumerable recesses 36.
- the output can be further increased, the rotation speed can be reduced for preventing noise and vibration, the viscosity of lubricating oil can be reduced for improving efficiency, and the efficiency can be improved
- the sliding condition of the sliding member will be more severe in the future.
- the lubricating oil can not be sufficiently retained in the contact sliding portion 34, so the oil film is broken and the sliding occurs.
- the moving members 30, 32 may come in contact with each other.
- the sliding surface of the sliding member of the compressor is such that the entire surface is not sliding under the same sliding conditions (load, lubricating oil viscosity, speed), but the sliding surfaces are in contact with each other There are mixed regions where the lubrication condition is severe and regions where the lubrication condition is not severe such that the sliding surfaces are separated by an oil film. Therefore, it is difficult to obtain a sufficient effect even if the same recess is disposed in the entire sliding surface.
- the present invention has been made to solve the above-described conventional problems, and the sliding surface of the sliding member of the compressor is in a region where the lubricating state is severe due to the sliding conditions (load, lubricating oil viscosity, speed) Depending on the area that does not, the specifications of the recess, ie the size of the recess opening, the depth of the recess, and the ratio of the opening to the sliding surface of the sliding member (hereinafter referred to as the opening area ratio) are set optimally. And a recess is provided.
- the sliding surface of the sliding member is made to have an area for suppressing wear and further enhancing the reliability of the sliding member, and a region for further reducing friction loss, that is, fluid viscosity loss.
- An object of the present invention is to provide a highly reliable and low-loss sliding member by effectively reducing friction loss and wear.
- the sliding member of the present invention is divided into a region where lubrication is severe depending on sliding conditions and a region not having such a region on the sliding surface of the sliding member.
- a recess according to the specification is provided on the surface.
- lubricating oil is effectively exuded by surface pressure relief of the sliding surface and oil accumulation to suppress wear, and decrease in the contact area reduces fluid viscosity loss, As friction loss and wear can be effectively reduced, a sliding member with a low friction coefficient and high reliability can be provided.
- the perspective view schematic diagram of the sliding member in Embodiment 1 of this invention A schematic view of a friction test device for measuring friction characteristics Characteristic diagram showing the sliding state of the sliding member according to the first embodiment and the sliding member of the comparative example Transverse cross-sectional view of a reciprocating compressor using the sliding member of the present invention Transverse cross-sectional view of a rotary compressor using the sliding member of the present invention Transverse cross-sectional view of a scroll compressor using the sliding member of the present invention Top view of fixed scroll of scroll compressor using sliding member of the present invention Top view of fixed scroll of scroll compressor using sliding member of the present invention Top view of fixed scroll of scroll compressor using sliding member of the present invention Top view of fixed scroll of scroll compressor using sliding member of the present invention Top view of fixed scroll of scroll compressor using sliding member of the present invention Top view of fixed scroll of scroll compressor using sliding member of the present invention A schematic cross-sectional view of a conventional smooth sliding surface A schematic cross-sectional view of a sliding surface provided with a conventional recess
- a first aspect of the invention has two sliding members sliding on the sliding surfaces of each other, and at least one of the sliding surfaces is provided with a plurality of dimple-shaped recesses, the shape of the recesses or the recesses
- the second invention produces the same effect as that of the first invention because the recess different depending on the region has a different shape of at least one of the opening size and the recess depth.
- a third invention has a first region and a second region as the regions, and the first region has a lubrication condition that is more severe than that of the second region.
- the opening face of the recess is substantially circular, lubricating oil is likely to ooze out, and a sliding member having a low coefficient of friction and high reliability can be provided.
- the sliding member according to the first to fourth inventions is a member used for a reciprocating compressor, a rotary compressor, or a scroll compressor, so that it has a low coefficient of friction and is reliable.
- a high compressor can be provided.
- FIG. 1 is a schematic perspective view of the sliding surface of the sliding member according to the first embodiment of the present invention, and shows a first area A under severe lubrication conditions and a second area B under severe lubrication conditions.
- the present invention relates to two sliding members in which sliding surfaces slide with each other.
- the sliding surface 138 of at least one of the sliding members 132 is provided with a dimple-shaped recess 136.
- the sliding surface 138 comprises the sliding surface 138 a of the first area A and the sliding surface 138 b of the second area B.
- the first region A has stricter lubricating conditions than the second region B.
- the shapes of the recess 136a formed in the sliding surface 138a and the recess 136b formed in the sliding surface 138b are different from each other. That is, at least one of the opening size and the recess depth is different between the recess 136a and the recess 136b.
- FIG. 1 shows the case where the recess 136a and the recess 136b have different opening sizes and recess depths.
- the recess depth of the recess 136a formed in the first region A is shallower than the recess depth of the recess 136b formed in the second region B, and the opening dimension of the recess 136a in the first region A is
- the opening size of the recess 136 b in the area B of 2 is made larger.
- the opening area ratio by the recess 136a in the sliding surface 138a of the first area A is different from the opening area ratio by the recess 136b in the sliding surface 138b of the second area B.
- the opening area ratio is the ratio of the total area of the opening surface of the recess 136 to the area of the sliding surface 138.
- a part of the sliding surface 138 of the sliding member 132 is captured by a laser microscope to perform computer image processing.
- the opening area ratio is obtained by dividing the sum of the areas of the opening faces of the individual depressions 136 by the total area of the sliding face 138 used for image processing after separating the opening face by the depressions 136 and the flat face 137. .
- the opening area ratio in the first region A is the total area of the sliding surface 138a used for image processing, the sum of the areas of the opening surfaces of the individual recesses 136a after separating the opening surface of the recess 136a and the flat surface 137a. It can be obtained by dividing by.
- the opening area ratio in the second region B is the total area of the sliding surface 138b used for image processing, the sum of the areas of the opening surfaces of the individual recesses 136b after separating the opening surface of the recess 136b and the flat surface 137b. It can be obtained by dividing by. In FIG. 1, the opening area ratio in the first region A is smaller than the opening area ratio in the second region B.
- dimple-like recessed portions 136a having a shallow depth are provided with a smaller opening area ratio as compared to the second region B where the lubricating conditions are not severe (for example, The diameter is about 0.2 mm, the depth is about 1 to 3 ⁇ m, the opening area ratio is about 10 to 25%).
- the diameter is about 0.2 mm, the depth is about 1 to 3 ⁇ m, the opening area ratio is about 10 to 25%.
- dimple-shaped concave portions 136b having a deep depth are provided with an increase in the open area ratio as compared with the first region A in which the lubricating conditions are severe.
- the diameter is within 0.15 mm to 0.3 mm, the depth is about 3 to 10 ⁇ m, the opening area ratio is about 20 to 50%).
- the shape of the opening is substantially circular. This is because the lubricating oil tends to exude.
- FIG. 2 is a perspective view of a friction test device for measuring friction characteristics.
- the friction characteristics of the sliding member 132 in which the concave portion 136 was formed by removal processing such as laser and etching, shot processing, and plastic processing such as press were evaluated by a ring-on-disk type experimental apparatus.
- a ring-shaped sliding member 12 and a disk-shaped sliding member 10 are attached to the friction test device shown in FIG. 2 as two sliding members.
- the ring-shaped sliding member 12 is rotated in a predetermined direction by the rotational force transmitted through the driving member 14 and the pin 16 and receives a load from above through the stationary shaft 18.
- a lubricating oil (not shown) is present between the two sliding members 10 and 12.
- a through hole 23 is provided on the side surface of the ring-shaped sliding member 12. Lubricating oil is appropriately supplied to the inner peripheral surface of the ring-shaped sliding member 12 from the microsyringe 24 inserted into the through hole 23 on the side surface of the ring-shaped sliding member 12, and the centrifugal force due to the rotation of the disk-shaped sliding member 10. Flows into the contact sliding portion of the two sliding members.
- a guide portion 20 provided concentrically above the disc-like sliding member 10 and the ring-like sliding member 12 bears the bearing of the stationary shaft 18.
- the ball bearing 22 is responsible for an aligning mechanism for bringing the ring-shaped sliding member 12 and the disk-shaped sliding member 10 into contact with each other without any contact.
- the experimental conditions by the said friction experiment apparatus were as follows in order to measure the friction coefficient in boundary lubrication, mixed lubrication, and fluid lubrication.
- the load is 6N to 110N
- the speed is 0.06 to 0.6m / sec
- the viscosity is 4.6 to 130mm 2 / sec
- the oil supply is 0.12cm 3 / min (0.03cm 3 ⁇ 4 times / Minutes).
- the ring-shaped sliding member 12 was ground-finished with an outer diameter of 25.6 mm, an inner diameter of 20 mm, and a material of FC200 (with a hardness of about HB 180) and a surface roughness of about Ra 0.2.
- the disc-like sliding member 10 is subjected to lapping after grinding with an outer diameter of 27 mm, a material of FC 250 (hardness: about 200) and a surface roughness of about Ra 0.2.
- a cross-shaped groove (not shown) is provided in the contact surface of the ring-shaped sliding member 12 with the disk-shaped sliding member 10.
- the lubricating oil was supplied in the same amount in all experiments.
- the relative sliding speed of the ring sliding member 12 and the disk-shaped sliding member 10 and the viscosity and contact pressure of the lubricating oil were changed.
- the opening area ratio is the ratio of the total area of the opening of the recess 136 to the area of the sliding surface 138 where the ring-shaped sliding member 12 and the disk-shaped sliding member 10 contact.
- a part of the sliding surface 138 of the sliding member was taken in by a laser microscope to perform computer image processing.
- the opening area ratio is obtained by dividing the sum of the opening areas of the openings of the concave portions 136 and the flat portions 137 and then dividing the sum of the opening areas of the openings of the individual concave portions 136 by the total area of the sliding surface 138 used for image processing. It has gained.
- the average value of the opening area ratio obtained by changing a measurement location and measuring several times was made into the representative value in the conditions.
- the surface roughness indicates the average value of the results measured several times with a stylus type shape measuring machine, and the depth of the recess 136 indicates the average value of the results measured several times with the laser microscope.
- FIG. 3 is a characteristic view of the coefficient of friction with the form of the sliding surface in the embodiment of the present invention as a parameter, and shows the number of bearing characteristics on the x axis and the coefficient of friction on the y axis.
- the bearing characteristic number is a non-dimensional number obtained by dividing the product of viscosity and speed of lubricating oil by surface pressure, and is an index of the state of lubrication. From the fluid lubrication area where the metal surface is separated by oil film as the number of bearing characteristics decreases, the oil film becomes thinner and mixed lubrication area where metal surface contact occurs, boundary lubrication where the oil film is very small and metal contact is excessive Change to the area.
- condition 3 shows the results of the condition 1 ( ⁇ ), the condition 2 ( ⁇ ) and the conventional condition 3 ( ⁇ ⁇ ) according to the first embodiment.
- the opening diameter of the recess 136 is 0.184 mm, the opening area ratio is 16%, the surface roughness Ra of the sliding surface 138 is 0.21, and the depth of the recess 136 is 1.2 ⁇ m.
- Condition 2 is that the opening diameter of the recess 136 is 0.176 mm, the opening area ratio is 35%, the surface roughness Ra of the sliding surface 138 is 0.23, and the depth of the recess 136 is 9.4 ⁇ m.
- Condition 3 is a conventional smooth surface without concave processing, and the surface roughness of the sliding surface 138 is Ra 0.2.
- the coefficient of friction is lower than that of a smooth surface by selecting the dimple specifications that match the bearing characteristic number, that is, the distribution of the loading condition, in one sliding portion and arranging them on the sliding surface.
- the wear state of the sliding surface 138 can be alleviated as well as suppressing the fluctuation and unstable sliding.
- the present invention is applicable to various sliding members of various devices, and the material and surface properties (initial surface roughness) of the sliding member, operating conditions, supply state of lubricating oil and oiliness (viscosity and Depending on the oil type, etc., it is necessary to determine the appropriate elements of the recess 136.
- a sliding member of a reciprocating compressor which is one of refrigeration cycle compressors, can be mentioned.
- FIG. 4 shows a cross-sectional view of the reciprocating compressor.
- the shaft main shaft 151 and the main bearing 152 have a cantilever bearing structure, so that the upper and lower ends of the main bearing 152 may come into contact with one another. Also, both materials are made of cast iron.
- the shaft main shaft 151 is subjected to a manganese phosphate coating treatment on its surface, and the shaft main shaft 151 is slightly lower in hardness than the main bearing 152.
- the sliding surface of the shaft main shaft 151 and the sliding surface of the slide bearing 152 are both finished to have a surface roughness Ra of 0.5 or less.
- the crankshaft is inclined within the main bearing 152 in the suction compression stroke of the refrigerant, whereby the thrust sliding surface 154 on the shaft main shaft 151 side and the outer periphery of the thrust sliding surface 155 on the main bearing 152 side One side contact may occur, and oil film pressure is less likely to occur due to planar contact.
- the thrust sliding surface 154 on the shaft main shaft 151 side and the thrust sliding surface 155 on the main bearing 152 side are both made of cast iron, and the thrust sliding surface 154 on the main shaft side is generally subjected to a manganese phosphate coating treatment The hardness of the thrust sliding surface 154 on the shaft main shaft 151 side is slightly lower.
- the thrust sliding surfaces 154 and 155 are both finished to have a surface roughness Ra of 0.5 or less.
- a partial contact may occur at the upper and lower ends of the connecting rod large end hole 157 in the suction compression stroke of the refrigerant.
- the shaft eccentric shaft 156 is made of cast iron
- the connecting rod 158 is made of aluminum alloy
- the surface of the shaft eccentric shaft 156 and the surface of the connecting rod large end hole 157 are both finished to have a surface roughness Ra of 0.5 or less.
- the piston pin 159 swings in the connecting rod small end hole 160 with respect to the piston pin 159 and the connecting rod small end hole 160, so the oil film is difficult to be formed compared to rotational movement in a fixed direction, and the sliding area is other
- the contact pressure is smaller and smaller than that of the sliding portion.
- the piston pin 159 is made of chrome steel, and the connecting rod 158 is made of aluminum alloy.
- the sliding surface of the piston pin 159 and the sliding surface of the connecting rod small end hole 160 are both finished to have a surface roughness Ra of 0.5 or less.
- the piston pin 159 is generally surface hardened or surface hardened by nitriding or the like.
- the crankshaft 163 is inclined within the main bearing 152 in the suction compression stroke of the refrigerant, and the piston is inclined in the vertical direction as viewed from the side of the reciprocating compressor 150 One part may occur in a part.
- the piston 161 is made of sintered iron, and the surface thereof is treated with manganese phosphate.
- One cylinder bore 162 is made of cast iron and has a somewhat lower hardness than the piston 161.
- the sliding surface of the piston 161 and the sliding surface of the cylinder bore 162 are both finished to have a surface roughness Ra of 0.5 or less.
- the present invention is considered to be effective for all possible sliding parts. That is, in a boundary lubrication area and a part where sliding in a mixed lubrication area (sliding members contact and slide) is assumed (discrimination is possible by observing the surface condition after driving)
- the recess area has a small opening area and a shallow recess depth, and the opening area is large and the recess depth is large in the fluid lubrication area (the area where sliding is assumed to be separated by the oil film of the sliding member) It is considered extremely effective to arrange a deep recess.
- the lubrication condition can be improved by providing the recess having the and the depth.
- the sliding member corresponding to the fluid lubrication region is provided with a recess having an opening area ratio, surface roughness, and depth corresponding to the operating rotational speed, surface pressure, actual use viscosity, etc. A shear force can be reduced, and a reciprocating compressor 150 with high efficiency and high reliability can be realized.
- FIG. 5 shows a cross-sectional view of the rotary compressor.
- the following is generally used as a sliding member of the current rotary compressor 170.
- the shaft main shaft 171 and the shaft sub-shaft 173 are integrally formed and made of cast iron, and the sliding surface of the shaft main shaft 171 and the sliding surface of the shaft sub-shaft 173 are treated with a manganese phosphate coating.
- One main bearing 172 and the secondary bearing 174 are made of sintered iron and have lower hardness than the shaft main shaft 171 and the shaft secondary shaft 173.
- the sliding surface of the main bearing 172 and the sliding surface of the sub bearing 174 are both finished to have a surface roughness Ra of 0.5 or less.
- the vane side surface 175 and the cylinder vane groove 176 reciprocate, it is difficult for oil film pressure to be generated.
- the vane side surface 175 is made of alloy steel, and the cylinder vane groove 176 is made of cast iron.
- the vane side surface 175 is finished to a surface roughness Ra of 0.5 or less, and the cylinder vane groove 176 is finished to Ra1 or less.
- the surface pressure of the vane tip 177 and the roller 178 becomes extremely high due to the line contact sliding.
- the vane tip 177 is made of alloy steel, and the sliding surface (tip) is hardened by forming a ceramic film by PVD or CVD.
- One roller 178 is made of cast iron. The sliding surface of the vane tip 177 and the sliding surface of the roller 178 are both finished to have a surface roughness Ra of 0.5 or less.
- the present invention is considered to be effective for all possible sliding parts. That is, in a boundary lubrication area and a part where sliding in a mixed lubrication area (sliding members contact and slide) is assumed (discrimination is possible by observing the surface condition after driving)
- the recess area has a small opening area and a shallow recess depth, and the opening area is large and the recess depth is large in the fluid lubrication area (the area where sliding is assumed to be separated by the oil film of the sliding member) It is considered extremely effective to arrange a deep recess.
- the appropriate opening area ratio, the surface roughness, and the depth corresponding to the operating rotation speed, the surface pressure, the actual use viscosity, etc., on the opposite sliding member, with respect to the parts that easily come into contact The lubrication can be improved by providing the recess having the taper.
- the sliding member corresponding to the fluid lubrication region is provided with a recess having an opening area ratio, surface roughness, and depth corresponding to the operating rotational speed, surface pressure, actual use viscosity, etc. A shear force can be reduced, and a rotary compressor 170 with high efficiency and high reliability can be realized.
- FIG. 6 shows a cross-sectional view of the scroll compressor.
- the shaft main shaft 181 and the main bearing 182, the shaft eccentric shaft 183 and the eccentric bearing 184, and the shaft sub shaft 185 and the sub bearing 186 are structurally at the upper and lower ends of the main bearing 182, the eccentric bearing 184 and the sub bearing 186 Hit is easy to happen.
- the shaft main shaft 181, the shaft eccentric shaft 183, and the shaft countershaft 185 are all made of surface hardened alloy steel.
- the one main bearing 182, the eccentric bearing 184, and the sub bearing 186 are all composites of resin and carbon with the metal back metal.
- the sliding surface of the shaft main shaft 181, the sliding surface of the shaft eccentric shaft 183, and the sliding surface of the shaft countershaft 186 are all finished to have a surface roughness Ra of 0.5 or less.
- the oil film pressure of the thrust bearing surface 190 formed between the fixed scroll 188 and the orbiting scroll 189 pressed against the fixed scroll 188 by the compressed gas from the main bearing 182 side is relatively flat due to flat contact. It is hard to occur. Further, since the outer peripheral portion is a low pressure and the inner peripheral portion is a high pressure, which is characteristic of the scroll compressor, the thrust bearing surface 190 is a sliding surface on which the load is easily changed.
- the fixed scroll 188 is made of cast iron
- the orbiting scroll 189 is made of aluminum alloy.
- the sliding surface of the fixed scroll 188 and the sliding surface of the orbiting scroll 189 are both finished to have a surface roughness Ra of 0.5 or less.
- the present invention is considered to be effective for all possible sliding parts. That is, in a boundary lubrication area and a part where sliding in a mixed lubrication area (sliding members contact and slide) is assumed (discrimination is possible by observing the surface condition after driving)
- the recess area has a small opening area and a shallow recess depth, and the opening area is large and the recess depth is large in the fluid lubrication area (the area where sliding is assumed to be separated by the oil film of the sliding member) It is considered extremely effective to arrange a deep recess.
- the lubrication can be improved by providing the recess having the taper.
- the sliding member corresponding to the fluid lubrication region is provided with a recess having an opening area ratio, surface roughness, and depth corresponding to the operating rotational speed, surface pressure, actual use viscosity, etc. The shear force can be reduced, and high efficiency and high reliability of the scroll compressor 180 having high efficiency and high reliability can be realized.
- the oil film is thin and metal contact occurs. Accordingly, in the area of boundary lubrication and mixed lubrication, it is possible to observe specular wear because the roughness (convex portion) is worn and the powder generated by the wear causes scratches. The powder generated by this abrasion scrapes the mating material and adheres to the mating material, and if the coagulated powder is pulled away at a stretch, a large scratch will occur. In the case of mirror surface wear, the accumulation of oil is eliminated and the oil film is less likely to be formed, so that adhesion is likely to occur. Finally, a large scratch is generated, wear progresses, and the reliability of the sliding member is greatly impaired.
- the degree of abrasion on the inner circumferential side 191 is lighter than in the state without dimples, and it can be said that the lubricity is also improved, and the reliability is improved.
- the dimples are also effective in capturing the powder generated by the wear, as the minute powder generated by the wear is confirmed from the observation in the concave portion after the operation.
- the sliding member has two sliding members on which the sliding surfaces slide with each other, and at least one of the sliding surfaces has a smaller opening area and a recessed portion in a region where the lubrication condition is relatively severe. A shallow recess is provided. As a result, the load is received by the flat portion on the sliding surface, and the lubricating oil held in the concave portion exudes to the flat portion, so that friction loss and the like can be obtained even under more severe sliding conditions. Wear can be reduced. On the other hand, in the region where the lubrication condition is not so severe, the opening area is large and the recess depth is deep.
- the area of the smooth surface can be reduced, and friction loss and wear can be reduced by the viscosity resistance of the lubricating oil becoming low and the lubricating oil held in the concave part permeating out to the flat part.
- the friction loss and the wear can be reduced more than the sliding member provided with.
- the sliding surface of the sliding member has an area for suppressing wear and further enhancing reliability, and an area for further reducing friction loss, that is, fluid viscosity loss, and the friction is effectively reduced. Loss and wear can be reduced, and a reliable sliding member can be provided.
- the present invention is applicable to various devices in which the sliding member is used, ie, various devices in various technical fields including compressors for refrigeration cycles.
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Abstract
It is anticipated that sliding conditions for sliding members will become harsher in the future. If sliding in a borderline lubrication state, in which maintaining adequate lubricating oil between sliding surfaces is not possible, and the oil film is ruptured and the sliding members come in contact with each other, continues for a long time, adhesion of abrasion powder and abrasive frictional wear may proceed, ultimately leading to locking due to seizure or to abnormal frictional wear. In the present invention, by appropriately setting the shape (size, depth, opening area) of recesses according to the sliding load rather than simply providing countless identical recesses on the surface of the sliding member, a highly efficient, highly reliable sliding member is provided, wherein frictional loss and wear are reduced even under harsher sliding conditions.
Description
本発明は、摺動部材の表面形状に関し、特に冷凍サイクル用圧縮機などにおける装置に対し、主として金属材料からなる摺動部材の摺動面に関する。
The present invention relates to the surface shape of a sliding member, and in particular to a sliding surface of a sliding member mainly made of a metal material with respect to an apparatus in a compressor for a refrigeration cycle and the like.
摺動部材の摩擦損失を低減させることは、装置の効率向上、及び信頼性向上のために必要である。例えば、冷凍冷蔵庫などに用いられるレシプロ圧縮機の場合、一般に使用される回転数である1500から3000rpmでは、摺動部材間に存在する油膜の厚さは1から2μm程度あるいはそれ以下とされている。
従来から摺動部材の摩擦損失を低減させるため、接触する摺動面の微細な凹凸を除去して可能な限り平滑にする努力がなされていた。
一方で、摺動部材の摩擦損失を低減させるため、平滑化された摺動部材の摺動面に凹部を形成するための加工を施す技術が提案されている。具体的には、断面が略円弧状の無数の凹部を摺動部材の摺動面に形成する技術が提案されている(例えば、特許文献1参照)。 Reducing the friction loss of the sliding member is necessary to improve the efficiency and reliability of the device. For example, in the case of a reciprocating compressor used for a refrigerator-freezer, etc., the thickness of the oil film existing between the sliding members is about 1 to 2 μm or less at the commonly used rotation speed of 1500 to 3000 rpm .
In the past, in order to reduce the friction loss of the sliding member, efforts have been made to remove asperity as much as possible by removing fine irregularities on the contacting sliding surface.
On the other hand, in order to reduce the friction loss of the sliding member, there has been proposed a technique of processing for forming a recess on the sliding surface of the smoothed sliding member. Specifically, a technique has been proposed in which an infinite number of concave portions having a substantially arc-shaped cross section are formed on the sliding surface of the sliding member (see, for example, Patent Document 1).
従来から摺動部材の摩擦損失を低減させるため、接触する摺動面の微細な凹凸を除去して可能な限り平滑にする努力がなされていた。
一方で、摺動部材の摩擦損失を低減させるため、平滑化された摺動部材の摺動面に凹部を形成するための加工を施す技術が提案されている。具体的には、断面が略円弧状の無数の凹部を摺動部材の摺動面に形成する技術が提案されている(例えば、特許文献1参照)。 Reducing the friction loss of the sliding member is necessary to improve the efficiency and reliability of the device. For example, in the case of a reciprocating compressor used for a refrigerator-freezer, etc., the thickness of the oil film existing between the sliding members is about 1 to 2 μm or less at the commonly used rotation speed of 1500 to 3000 rpm .
In the past, in order to reduce the friction loss of the sliding member, efforts have been made to remove asperity as much as possible by removing fine irregularities on the contacting sliding surface.
On the other hand, in order to reduce the friction loss of the sliding member, there has been proposed a technique of processing for forming a recess on the sliding surface of the smoothed sliding member. Specifically, a technique has been proposed in which an infinite number of concave portions having a substantially arc-shaped cross section are formed on the sliding surface of the sliding member (see, for example, Patent Document 1).
以下、図面を用いてこれらの従来技術を説明する。図10、図11は、相互に摺動する摺動部材が潤滑油による油膜(図示省略)を介して対向している状態を示している。
図10は摺動部材32と対向する摺動部材30の摺動面をともに平滑にした状態を示している。
図11は、対向する摺動部材30の摺動面を平滑にし、もう一方の摺動部材32の摺動面38に無数の凹部36を設けた様子を示している。特許文献1によれば、接触摺動部34に潤滑油を供給すると、潤滑油は表面張力により無数に形成された凹部36にて油玉となり、荷重が加えられると、各凹部36の隣接する油玉が互いに連結し、摺動面全域に油膜が形成される。 Hereinafter, these conventional techniques will be described using the drawings. FIG. 10 and FIG. 11 show a state in which the sliding members sliding relative to each other are opposed via an oil film (not shown) of lubricating oil.
FIG. 10 shows a state in which the sliding surfaces of the slidingmember 30 facing the sliding member 32 are both smoothed.
FIG. 11 shows that the sliding surface of the opposing slidingmember 30 is made smooth and the sliding surface 38 of the other sliding member 32 is provided with innumerable recesses 36. According to Patent Document 1, when lubricating oil is supplied to the contact sliding portion 34, the lubricating oil becomes oil balls in the concave portions 36 formed innumerably by surface tension, and when a load is applied, the concave portions 36 are adjacent The oil balls are connected to each other, and an oil film is formed on the entire sliding surface.
図10は摺動部材32と対向する摺動部材30の摺動面をともに平滑にした状態を示している。
図11は、対向する摺動部材30の摺動面を平滑にし、もう一方の摺動部材32の摺動面38に無数の凹部36を設けた様子を示している。特許文献1によれば、接触摺動部34に潤滑油を供給すると、潤滑油は表面張力により無数に形成された凹部36にて油玉となり、荷重が加えられると、各凹部36の隣接する油玉が互いに連結し、摺動面全域に油膜が形成される。 Hereinafter, these conventional techniques will be described using the drawings. FIG. 10 and FIG. 11 show a state in which the sliding members sliding relative to each other are opposed via an oil film (not shown) of lubricating oil.
FIG. 10 shows a state in which the sliding surfaces of the sliding
FIG. 11 shows that the sliding surface of the opposing sliding
しかしながら、上記従来の圧縮機などでは、さらなる高出力化や、騒音や振動防止のための低回転化や、効率向上のための潤滑油の低粘度化や、摺動部分の削減による高効率化を図ることで、却って摺動部材の摺動状況が今後一層過酷になることが想定される。
図10のように、摺動部材30、32間の摺動面が互いに平滑な場合では、接触摺動部34に潤滑油を十分に保持することができず、このため油膜が破断して摺動部材30、32同士が接触することがある。このような摺動部材30、32間で境界潤滑領域での摺動状態が長時間継続すると、摩耗粉の凝着やアブレシブ摩耗が進行して、最終的にいわゆる焼き付きによるロックや、異常摩耗に至ることがある。
また、図11のように、無数の凹部36を摺動面38に設けた場合、摺動開始からしばらく経過すると、摩擦係数が、急激に増加に転じたり、摺動開始直後から摩擦係数が大きな変動を伴いながら高い値に推移することがある。その結果、摺動部材30、32の摺動面に激しい摩耗が生じることがある。 However, in the above-mentioned conventional compressors and the like, the output can be further increased, the rotation speed can be reduced for preventing noise and vibration, the viscosity of lubricating oil can be reduced for improving efficiency, and the efficiency can be improved On the contrary, it is assumed that the sliding condition of the sliding member will be more severe in the future.
As shown in FIG. 10, in the case where the sliding surfaces between the sliding members 30 and 32 are smooth with each other, the lubricating oil can not be sufficiently retained in the contact sliding portion 34, so the oil film is broken and the sliding occurs. The moving members 30, 32 may come in contact with each other. When the sliding condition in the boundary lubrication area continues for a long time between the sliding members 30 and 32 as described above, adhesion of wear powder and abrasive wear progress, and finally, so-called locking due to seizing or abnormal wear is caused. There is everything.
Further, as shown in FIG. 11, when theinnumerable recesses 36 are provided on the sliding surface 38, the friction coefficient starts to increase rapidly after a while from the start of sliding, or the coefficient of friction is large immediately after the start of sliding. It may change to a high value with fluctuations. As a result, severe wear may occur on the sliding surfaces of the sliding members 30, 32.
図10のように、摺動部材30、32間の摺動面が互いに平滑な場合では、接触摺動部34に潤滑油を十分に保持することができず、このため油膜が破断して摺動部材30、32同士が接触することがある。このような摺動部材30、32間で境界潤滑領域での摺動状態が長時間継続すると、摩耗粉の凝着やアブレシブ摩耗が進行して、最終的にいわゆる焼き付きによるロックや、異常摩耗に至ることがある。
また、図11のように、無数の凹部36を摺動面38に設けた場合、摺動開始からしばらく経過すると、摩擦係数が、急激に増加に転じたり、摺動開始直後から摩擦係数が大きな変動を伴いながら高い値に推移することがある。その結果、摺動部材30、32の摺動面に激しい摩耗が生じることがある。 However, in the above-mentioned conventional compressors and the like, the output can be further increased, the rotation speed can be reduced for preventing noise and vibration, the viscosity of lubricating oil can be reduced for improving efficiency, and the efficiency can be improved On the contrary, it is assumed that the sliding condition of the sliding member will be more severe in the future.
As shown in FIG. 10, in the case where the sliding surfaces between the sliding
Further, as shown in FIG. 11, when the
また、圧縮機の摺動部材の摺動面は、その全領域が同じ摺動条件(荷重、潤滑油粘度、速度)で摺動しているのではなく、摺動面同士が接触するような潤滑状態が厳しい領域と、摺動面同士が油膜で隔てられているような潤滑状態が厳しくない領域が混在している。従って、摺動面全域に同じ凹部を配設しても、十分な効果を得ることは困難であった。
Also, the sliding surface of the sliding member of the compressor is such that the entire surface is not sliding under the same sliding conditions (load, lubricating oil viscosity, speed), but the sliding surfaces are in contact with each other There are mixed regions where the lubrication condition is severe and regions where the lubrication condition is not severe such that the sliding surfaces are separated by an oil film. Therefore, it is difficult to obtain a sufficient effect even if the same recess is disposed in the entire sliding surface.
本発明は、上記従来の課題を解決するためになされたもので、圧縮機の摺動部材の摺動面に、摺動条件(荷重、潤滑油粘度、速度)により、潤滑状態が厳しい領域とそうでない領域に応じて、凹部の仕様、即ち凹部開口部の大きさ、凹部の深さ、及び摺動部材の摺動面に対する開口部の占める割合(以下、開口面積率という)を最適に設定して凹部を配設するものである。これにより、摩耗を抑制して摺動部材の信頼性を更に高める作用を行う領域と、摩擦損失、即ち流体粘性損失を更に減らす作用を行う領域とを摺動部材の摺動面に併せ持たせ、効果的に摩擦損失や摩耗を低減し、信頼性が高く損失の少ない摺動部材を提供することを目的とする。
The present invention has been made to solve the above-described conventional problems, and the sliding surface of the sliding member of the compressor is in a region where the lubricating state is severe due to the sliding conditions (load, lubricating oil viscosity, speed) Depending on the area that does not, the specifications of the recess, ie the size of the recess opening, the depth of the recess, and the ratio of the opening to the sliding surface of the sliding member (hereinafter referred to as the opening area ratio) are set optimally. And a recess is provided. Thereby, the sliding surface of the sliding member is made to have an area for suppressing wear and further enhancing the reliability of the sliding member, and a region for further reducing friction loss, that is, fluid viscosity loss. An object of the present invention is to provide a highly reliable and low-loss sliding member by effectively reducing friction loss and wear.
前記従来の課題を解決するために、本発明の摺動部材は、摺動部材の摺動面において、摺動条件により潤滑状態が厳しい領域とそうでない領域に分け、各々の領域に対応した凹部仕様による凹部をその表面に施している。これにより、接触面の面圧緩和や油溜まりで効果的に潤滑油を滲み出させて摩耗を抑制させるとともに、接触面積の減少により流体粘性損失を低減させて、効果的に摩擦損失や摩耗を低減することができる。
In order to solve the above-mentioned conventional problems, the sliding member of the present invention is divided into a region where lubrication is severe depending on sliding conditions and a region not having such a region on the sliding surface of the sliding member. A recess according to the specification is provided on the surface. As a result, lubricating oil is effectively exuded by surface pressure relief of the contact surface and oil accumulation to suppress wear, and decrease in the contact area reduces fluid viscosity loss, effectively resulting in friction loss and wear. It can be reduced.
本発明の摺動部材によれば、摺動面の面圧緩和や油溜まりで効果的に潤滑油を滲み出させて摩耗を抑制させるとともに、接触面積の減少により流体粘性損失を低減させて、効果的に摩擦損失や摩耗を低減することができるので、摩擦係数が低くてかつ信頼性の高い摺動部材を提供できる。
According to the sliding member of the present invention, lubricating oil is effectively exuded by surface pressure relief of the sliding surface and oil accumulation to suppress wear, and decrease in the contact area reduces fluid viscosity loss, As friction loss and wear can be effectively reduced, a sliding member with a low friction coefficient and high reliability can be provided.
10 ディスク状摺動部材
12 リング状摺動部材
132 摺動部材
136,136a,136b 凹部
137,137a,137b 平坦部
138,138a,138b 摺動面
150 レシプロ圧縮機
170 ロータリー圧縮機
180 スクロール圧縮機
188 固定スクロール
189 旋回スクロール
190 スラスト軸受面
191 内周側
192 外周側 DESCRIPTION OFSYMBOLS 10 Disc-like sliding member 12 Ring-like sliding member 132 Sliding member 136, 136a, 136b Concave part 137, 137a, 137b Flat part 138, 138a, 138b Sliding surface 150 Reciprocating compressor 170 Rotary compressor 180 Scroll compressor 188 Fixed scroll 189 Orbiting scroll 190 Thrust bearing surface 191 Inner circumferential side 192 Outer circumferential side
12 リング状摺動部材
132 摺動部材
136,136a,136b 凹部
137,137a,137b 平坦部
138,138a,138b 摺動面
150 レシプロ圧縮機
170 ロータリー圧縮機
180 スクロール圧縮機
188 固定スクロール
189 旋回スクロール
190 スラスト軸受面
191 内周側
192 外周側 DESCRIPTION OF
第1の発明は、互いの摺動面を摺動する2つの摺動部材を有し、少なくとも一方の前記摺動面に、ディンプル状の複数の凹部を設け、前記凹部の形状又は前記凹部による開口面積率が領域により異ならせることにより、摺動面の面圧緩和や油溜まりで効果的に潤滑油を滲み出させて摩耗を抑制させるとともに、接触面積の減少により流体粘性損失を低減させて、効果的に摩擦損失や摩耗を低減することができるので、摩擦係数が低くてかつ信頼性の高い摺動部材を提供できる。
A first aspect of the invention has two sliding members sliding on the sliding surfaces of each other, and at least one of the sliding surfaces is provided with a plurality of dimple-shaped recesses, the shape of the recesses or the recesses By making the opening area ratio different depending on the area, lubricating oil is effectively exudeed by surface pressure relaxation of the sliding surface and oil accumulation to suppress wear, and the fluid viscosity loss is reduced by reducing the contact area. Since the friction loss and the wear can be effectively reduced, a sliding member having a low friction coefficient and high reliability can be provided.
第2の発明は、前記領域によって異なる前記凹部が、開口寸法及び凹部深さの少なくとも一方の形状が異なることにより、第1の発明と同じ効果を生じる。
The second invention produces the same effect as that of the first invention because the recess different depending on the region has a different shape of at least one of the opening size and the recess depth.
第3の発明は、前記領域として、第1の領域と第2の領域とを有し、前記第1の領域が、前記第2の領域よりも潤滑条件が厳しい場合に、前記第1の領域に形成される前記凹部の前記凹部深さを、前記第2の領域に形成される前記凹部の前記凹部深さよりも浅くし、前記第1の領域における前記開口面積率を、前記第2の領域における前記開口面積率よりも小さくしたことにより、摩擦係数が低くてかつ信頼性の高い摺動部材を提供することができる。
A third invention has a first region and a second region as the regions, and the first region has a lubrication condition that is more severe than that of the second region. Making the recess depth of the recess formed in the second region shallower than the recess depth of the recess formed in the second region, and setting the opening area ratio in the first region to the second region By making the opening area ratio smaller than in the above, it is possible to provide a sliding member having a low friction coefficient and high reliability.
第4の発明は、前記凹部の開口面が略円形であることにより、潤滑油が滲み出しやすくなり、更に、摩擦係数が低くてかつ信頼性の高い摺動部材を提供することができる。
According to a fourth aspect of the present invention, since the opening face of the recess is substantially circular, lubricating oil is likely to ooze out, and a sliding member having a low coefficient of friction and high reliability can be provided.
第5の発明は、第1から第4の発明に係る摺動部材は、レシプロ圧縮機、ロータリー圧縮機、又はスクロール圧縮機に用いられる部材であることにより、摩擦係数が低くてかつ信頼性の高い圧縮機を提供することができる。
In a fifth invention, the sliding member according to the first to fourth inventions is a member used for a reciprocating compressor, a rotary compressor, or a scroll compressor, so that it has a low coefficient of friction and is reliable. A high compressor can be provided.
以下、本発明の実施の形態について、図面を参照しながら説明する。尚、この実施の形態によってこの発明が限定されるものではない。
Hereinafter, embodiments of the present invention will be described with reference to the drawings. The present invention is not limited by the embodiment.
(実施の形態1)
図1は本発明の実施の形態1における摺動部材の摺動面の斜視模式図であり、潤滑条件が厳しい第1の領域A及び潤滑条件が厳しくない第2の領域Bを示す。
本発明は、互いの摺動面が摺動する2つの摺動部材に関するものである。少なくとも一方の摺動部材132の摺動面138には、ディンプル状の凹部136が設けられている。
摺動面138は、第1の領域Aの摺動面138aと第2の領域Bの摺動面138bとからなる。ここでは第1の領域Aは、第2の領域Bよりも潤滑条件が厳しい場合とする。
摺動面138aに形成される凹部136aと摺動面138bに形成される凹部136bの形状は互いに異なる。すなわち凹部136aと凹部136bとは、開口寸法及び凹部深さの少なくとも一方が異なる。
図1では、凹部136aと凹部136bとは、開口寸法及び凹部深さが異なる場合を示している。
第1の領域Aに形成される凹部136aの凹部深さは、第2の領域Bに形成される凹部136bの凹部深さよりも浅くし、第1の領域Aにおける凹部136aの開口寸法を、第2の領域Bにおける凹部136bの開口寸法よりも大きくしている。Embodiment 1
FIG. 1 is a schematic perspective view of the sliding surface of the sliding member according to the first embodiment of the present invention, and shows a first area A under severe lubrication conditions and a second area B under severe lubrication conditions.
The present invention relates to two sliding members in which sliding surfaces slide with each other. The slidingsurface 138 of at least one of the sliding members 132 is provided with a dimple-shaped recess 136.
Thesliding surface 138 comprises the sliding surface 138 a of the first area A and the sliding surface 138 b of the second area B. Here, it is assumed that the first region A has stricter lubricating conditions than the second region B.
The shapes of the recess 136a formed in thesliding surface 138a and the recess 136b formed in the sliding surface 138b are different from each other. That is, at least one of the opening size and the recess depth is different between the recess 136a and the recess 136b.
FIG. 1 shows the case where the recess 136a and the recess 136b have different opening sizes and recess depths.
The recess depth of the recess 136a formed in the first region A is shallower than the recess depth of the recess 136b formed in the second region B, and the opening dimension of the recess 136a in the first region A is The opening size of the recess 136 b in the area B of 2 is made larger.
図1は本発明の実施の形態1における摺動部材の摺動面の斜視模式図であり、潤滑条件が厳しい第1の領域A及び潤滑条件が厳しくない第2の領域Bを示す。
本発明は、互いの摺動面が摺動する2つの摺動部材に関するものである。少なくとも一方の摺動部材132の摺動面138には、ディンプル状の凹部136が設けられている。
摺動面138は、第1の領域Aの摺動面138aと第2の領域Bの摺動面138bとからなる。ここでは第1の領域Aは、第2の領域Bよりも潤滑条件が厳しい場合とする。
摺動面138aに形成される凹部136aと摺動面138bに形成される凹部136bの形状は互いに異なる。すなわち凹部136aと凹部136bとは、開口寸法及び凹部深さの少なくとも一方が異なる。
図1では、凹部136aと凹部136bとは、開口寸法及び凹部深さが異なる場合を示している。
第1の領域Aに形成される凹部136aの凹部深さは、第2の領域Bに形成される凹部136bの凹部深さよりも浅くし、第1の領域Aにおける凹部136aの開口寸法を、第2の領域Bにおける凹部136bの開口寸法よりも大きくしている。
FIG. 1 is a schematic perspective view of the sliding surface of the sliding member according to the first embodiment of the present invention, and shows a first area A under severe lubrication conditions and a second area B under severe lubrication conditions.
The present invention relates to two sliding members in which sliding surfaces slide with each other. The sliding
The
The shapes of the recess 136a formed in the
FIG. 1 shows the case where the recess 136a and the recess 136b have different opening sizes and recess depths.
The recess depth of the recess 136a formed in the first region A is shallower than the recess depth of the recess 136b formed in the second region B, and the opening dimension of the recess 136a in the first region A is The opening size of the recess 136 b in the area B of 2 is made larger.
第1の領域Aの摺動面138aにおける凹部136aによる開口面積率と、第2の領域Bの摺動面138bにおける凹部136bによる開口面積率とは異なる。
開口面積率とは、摺動面138の面積に対する凹部136の開口面の総面積の割合のことである。摺動部材132の摺動面138の一部をレーザー顕微鏡にて取り込んでコンピュータ画像処理を行う。凹部136による開口面と、平坦面137を分別した後に、個々の凹部136の開口面の面積の総和を画像処理に用いた摺動面138の全面積で除することで、開口面積率を得る。尚、測定箇所を変えて数回計測して得られた開口面積率の平均値をその条件での代表値とした。
第1の領域Aにおける開口面積率は、凹部136aの開口面と、平坦面137aを分別した後に、個々の凹部136aの開口面の面積の総和を画像処理に用いた摺動面138aの全面積で除することで得ることができる。
第2の領域Bにおける開口面積率は、凹部136bの開口面と、平坦面137bを分別した後に、個々の凹部136bの開口面の面積の総和を画像処理に用いた摺動面138bの全面積で除することで得ることができる。
図1では、第1の領域Aにおける開口面積率を、第2の領域Bにおける開口面積率よりも小さくしている。 The opening area ratio by the recess 136a in thesliding surface 138a of the first area A is different from the opening area ratio by the recess 136b in the sliding surface 138b of the second area B.
The opening area ratio is the ratio of the total area of the opening surface of therecess 136 to the area of the sliding surface 138. A part of the sliding surface 138 of the sliding member 132 is captured by a laser microscope to perform computer image processing. The opening area ratio is obtained by dividing the sum of the areas of the opening faces of the individual depressions 136 by the total area of the sliding face 138 used for image processing after separating the opening face by the depressions 136 and the flat face 137. . In addition, the average value of the opening area ratio obtained by changing a measurement location and measuring several times was made into the representative value in the conditions.
The opening area ratio in the first region A is the total area of thesliding surface 138a used for image processing, the sum of the areas of the opening surfaces of the individual recesses 136a after separating the opening surface of the recess 136a and the flat surface 137a. It can be obtained by dividing by.
The opening area ratio in the second region B is the total area of the sliding surface 138b used for image processing, the sum of the areas of the opening surfaces of the individual recesses 136b after separating the opening surface of the recess 136b and the flat surface 137b. It can be obtained by dividing by.
In FIG. 1, the opening area ratio in the first region A is smaller than the opening area ratio in the second region B.
開口面積率とは、摺動面138の面積に対する凹部136の開口面の総面積の割合のことである。摺動部材132の摺動面138の一部をレーザー顕微鏡にて取り込んでコンピュータ画像処理を行う。凹部136による開口面と、平坦面137を分別した後に、個々の凹部136の開口面の面積の総和を画像処理に用いた摺動面138の全面積で除することで、開口面積率を得る。尚、測定箇所を変えて数回計測して得られた開口面積率の平均値をその条件での代表値とした。
第1の領域Aにおける開口面積率は、凹部136aの開口面と、平坦面137aを分別した後に、個々の凹部136aの開口面の面積の総和を画像処理に用いた摺動面138aの全面積で除することで得ることができる。
第2の領域Bにおける開口面積率は、凹部136bの開口面と、平坦面137bを分別した後に、個々の凹部136bの開口面の面積の総和を画像処理に用いた摺動面138bの全面積で除することで得ることができる。
図1では、第1の領域Aにおける開口面積率を、第2の領域Bにおける開口面積率よりも小さくしている。 The opening area ratio by the recess 136a in the
The opening area ratio is the ratio of the total area of the opening surface of the
The opening area ratio in the first region A is the total area of the
The opening area ratio in the second region B is the total area of the sliding surface 138b used for image processing, the sum of the areas of the opening surfaces of the individual recesses 136b after separating the opening surface of the recess 136b and the flat surface 137b. It can be obtained by dividing by.
In FIG. 1, the opening area ratio in the first region A is smaller than the opening area ratio in the second region B.
潤滑条件が厳しい第1の領域Aでは、潤滑条件が厳しくない第2の領域Bと比較して、深さの浅いディンプル状の凹部136aが、開口面積率を小さくして設けられている(例えば直径0.2mm前後、深さ1~3μm程度、開口面積率10~25%程度)。これにより、摺動面138上の平坦部にてその荷重を面で受け止めるとともに凹部136に保持された潤滑油が平坦部に滲み出ることで、より過酷な摺動条件の場合であっても摩擦損失や摩耗を低減することができる。
これに対し、潤滑条件が厳しくない第2の領域Bでは、潤滑条件が厳しい第1の領域Aと比較して、深さの深いディンプル状の凹部136bが、開口面積率を大きくして設けられている(例えば、直径0.15mm~0.3mm以内、深さ3~10μm程度、開口面積率20~50%程度)。これにより、平滑面の面積を減少させることができ、潤滑油の粘性抵抗が低くなるとともに凹部に保持された潤滑油が平坦部に滲み出ることで摩擦損失や摩耗を低減できる。なお、開口部の形状が略円形であることが好ましい。これは潤滑油が滲み出しやすくなるからである。 In the first region A where the lubricating conditions are severe, dimple-like recessed portions 136a having a shallow depth are provided with a smaller opening area ratio as compared to the second region B where the lubricating conditions are not severe (for example, The diameter is about 0.2 mm, the depth is about 1 to 3 μm, the opening area ratio is about 10 to 25%). As a result, the load is received by the flat portion on the slidingsurface 138 and the lubricating oil held in the recess 136 oozes out to the flat portion, thereby providing friction even under more severe sliding conditions. Loss and wear can be reduced.
On the other hand, in the second region B in which the lubricating conditions are not severe, dimple-shaped concave portions 136b having a deep depth are provided with an increase in the open area ratio as compared with the first region A in which the lubricating conditions are severe. (For example, the diameter is within 0.15 mm to 0.3 mm, the depth is about 3 to 10 μm, the opening area ratio is about 20 to 50%). As a result, the area of the smooth surface can be reduced, and the viscosity resistance of the lubricating oil decreases, and the lubricating oil held in the recess exudes to the flat portion, thereby reducing friction loss and wear. Preferably, the shape of the opening is substantially circular. This is because the lubricating oil tends to exude.
これに対し、潤滑条件が厳しくない第2の領域Bでは、潤滑条件が厳しい第1の領域Aと比較して、深さの深いディンプル状の凹部136bが、開口面積率を大きくして設けられている(例えば、直径0.15mm~0.3mm以内、深さ3~10μm程度、開口面積率20~50%程度)。これにより、平滑面の面積を減少させることができ、潤滑油の粘性抵抗が低くなるとともに凹部に保持された潤滑油が平坦部に滲み出ることで摩擦損失や摩耗を低減できる。なお、開口部の形状が略円形であることが好ましい。これは潤滑油が滲み出しやすくなるからである。 In the first region A where the lubricating conditions are severe, dimple-like recessed portions 136a having a shallow depth are provided with a smaller opening area ratio as compared to the second region B where the lubricating conditions are not severe (for example, The diameter is about 0.2 mm, the depth is about 1 to 3 μm, the opening area ratio is about 10 to 25%). As a result, the load is received by the flat portion on the sliding
On the other hand, in the second region B in which the lubricating conditions are not severe, dimple-shaped concave portions 136b having a deep depth are provided with an increase in the open area ratio as compared with the first region A in which the lubricating conditions are severe. (For example, the diameter is within 0.15 mm to 0.3 mm, the depth is about 3 to 10 μm, the opening area ratio is about 20 to 50%). As a result, the area of the smooth surface can be reduced, and the viscosity resistance of the lubricating oil decreases, and the lubricating oil held in the recess exudes to the flat portion, thereby reducing friction loss and wear. Preferably, the shape of the opening is substantially circular. This is because the lubricating oil tends to exude.
図2は、摩擦特性を測定する摩擦実験装置の斜視図である。レーザー、エッチング等の除去加工やショットブラスト、プレス等の塑性加工などにより凹部136が形成された摺動部材132の摩擦特性をリングオンディスク方式の実験装置にて評価した。
図2に示される摩擦実験装置には、2つの摺動部材として、リング状摺動部材12とディスク状摺動部材10が装着される。リング状摺動部材12は、駆動部材14とピン16を介して伝達される回転力により所定方向に回転するとともに、上方から静止軸18を介して荷重負荷を受ける。
したがって、リング状摺動部材12がディスク状摺動部材10に所定圧力で接触しつつディスク状摺動部材10が回転するので、リング状摺動部材12とディスク状摺動部材10の間に摩擦が生じる。尚、この2つの摺動部材10、12間には図示省略の潤滑油が存在している。リング状摺動部材12の側面に貫通穴23が設けられている。リング状摺動部材12の側面の貫通穴23に挿入されたマイクロシリンジ24から、潤滑油がリング状摺動部材12の内周面に適宜供給され、ディスク状摺動部材10の回転による遠心力により2つの摺動部材の接触摺動部に流入する。また、ディスク状摺動部材10及びリング状摺動部材12の同心円上方に設けたガイド部20は静止軸18の軸受を担っている。また、ボール軸受22はリング状摺動部材12とディスク状摺動部材10が片当りせずに面で接触させるための調心機構を担っている。 FIG. 2 is a perspective view of a friction test device for measuring friction characteristics. The friction characteristics of the slidingmember 132 in which the concave portion 136 was formed by removal processing such as laser and etching, shot processing, and plastic processing such as press were evaluated by a ring-on-disk type experimental apparatus.
A ring-shaped slidingmember 12 and a disk-shaped sliding member 10 are attached to the friction test device shown in FIG. 2 as two sliding members. The ring-shaped sliding member 12 is rotated in a predetermined direction by the rotational force transmitted through the driving member 14 and the pin 16 and receives a load from above through the stationary shaft 18.
Therefore, since the disk-shaped slidingmember 10 rotates while the ring-shaped sliding member 12 contacts the disk-shaped sliding member 10 with a predetermined pressure, the friction between the ring-shaped sliding member 12 and the disk-shaped sliding member 10 Will occur. A lubricating oil (not shown) is present between the two sliding members 10 and 12. A through hole 23 is provided on the side surface of the ring-shaped sliding member 12. Lubricating oil is appropriately supplied to the inner peripheral surface of the ring-shaped sliding member 12 from the microsyringe 24 inserted into the through hole 23 on the side surface of the ring-shaped sliding member 12, and the centrifugal force due to the rotation of the disk-shaped sliding member 10. Flows into the contact sliding portion of the two sliding members. Further, a guide portion 20 provided concentrically above the disc-like sliding member 10 and the ring-like sliding member 12 bears the bearing of the stationary shaft 18. Further, the ball bearing 22 is responsible for an aligning mechanism for bringing the ring-shaped sliding member 12 and the disk-shaped sliding member 10 into contact with each other without any contact.
図2に示される摩擦実験装置には、2つの摺動部材として、リング状摺動部材12とディスク状摺動部材10が装着される。リング状摺動部材12は、駆動部材14とピン16を介して伝達される回転力により所定方向に回転するとともに、上方から静止軸18を介して荷重負荷を受ける。
したがって、リング状摺動部材12がディスク状摺動部材10に所定圧力で接触しつつディスク状摺動部材10が回転するので、リング状摺動部材12とディスク状摺動部材10の間に摩擦が生じる。尚、この2つの摺動部材10、12間には図示省略の潤滑油が存在している。リング状摺動部材12の側面に貫通穴23が設けられている。リング状摺動部材12の側面の貫通穴23に挿入されたマイクロシリンジ24から、潤滑油がリング状摺動部材12の内周面に適宜供給され、ディスク状摺動部材10の回転による遠心力により2つの摺動部材の接触摺動部に流入する。また、ディスク状摺動部材10及びリング状摺動部材12の同心円上方に設けたガイド部20は静止軸18の軸受を担っている。また、ボール軸受22はリング状摺動部材12とディスク状摺動部材10が片当りせずに面で接触させるための調心機構を担っている。 FIG. 2 is a perspective view of a friction test device for measuring friction characteristics. The friction characteristics of the sliding
A ring-shaped sliding
Therefore, since the disk-shaped sliding
なお、上記摩擦実験装置による実験条件は境界潤滑、混合潤滑及び流体潤滑での摩擦係数を測定するため次の通りとした。荷重は6N~110Nとし、速度は0.06~0.6m/secとし、粘度は4.6~130mm2/secとし、オイル供給は0.12cm3/分(0.03cm3×4回/分)とした。
リング状摺動部材12は、外径が25.6mm、内径が20mm、材質をFC200(硬度HB180程度)で、表面粗さがRa0.2程度の研削仕上げとした。ディスク状摺動部材10は、外径27mm、材質をFC250(硬度HB200程度)で、表面粗さがRa0.2程度の研削加工後ラップ仕上げを行っている。リング状摺動部材12のディスク状摺動部材10との接触面には、潤滑油が摺動面に十分に行き渡るように十字状の溝(図示省略)を設けた。潤滑油の供給はどの実験でも同量で行った。
更に、油膜が形成され難く金属接触が生じるような摺動状態である境界潤滑、油膜が形成され金属接触が生じにくい摺動状態である流体潤滑、また、その遷移状態である混合潤滑の軸受特性値を得る為に、リング摺動部材12とディスク状摺動部材10の相対すべり速度と潤滑油の粘度と面圧を変化させた。 In addition, the experimental conditions by the said friction experiment apparatus were as follows in order to measure the friction coefficient in boundary lubrication, mixed lubrication, and fluid lubrication. The load is 6N to 110N, the speed is 0.06 to 0.6m / sec, the viscosity is 4.6 to 130mm 2 / sec, the oil supply is 0.12cm 3 / min (0.03cm 3 × 4 times / Minutes).
The ring-shaped slidingmember 12 was ground-finished with an outer diameter of 25.6 mm, an inner diameter of 20 mm, and a material of FC200 (with a hardness of about HB 180) and a surface roughness of about Ra 0.2. The disc-like sliding member 10 is subjected to lapping after grinding with an outer diameter of 27 mm, a material of FC 250 (hardness: about 200) and a surface roughness of about Ra 0.2. In the contact surface of the ring-shaped sliding member 12 with the disk-shaped sliding member 10, a cross-shaped groove (not shown) is provided so that the lubricating oil sufficiently spreads over the sliding surface. The lubricating oil was supplied in the same amount in all experiments.
Furthermore, the bearing characteristics of boundary lubrication in a sliding state in which an oil film is hard to form and metal contact occurs, fluid lubrication in an oil film formed and sliding state in which metal contact is hard to occur, and mixed lubrication in its transition state. In order to obtain the values, the relative sliding speed of thering sliding member 12 and the disk-shaped sliding member 10 and the viscosity and contact pressure of the lubricating oil were changed.
リング状摺動部材12は、外径が25.6mm、内径が20mm、材質をFC200(硬度HB180程度)で、表面粗さがRa0.2程度の研削仕上げとした。ディスク状摺動部材10は、外径27mm、材質をFC250(硬度HB200程度)で、表面粗さがRa0.2程度の研削加工後ラップ仕上げを行っている。リング状摺動部材12のディスク状摺動部材10との接触面には、潤滑油が摺動面に十分に行き渡るように十字状の溝(図示省略)を設けた。潤滑油の供給はどの実験でも同量で行った。
更に、油膜が形成され難く金属接触が生じるような摺動状態である境界潤滑、油膜が形成され金属接触が生じにくい摺動状態である流体潤滑、また、その遷移状態である混合潤滑の軸受特性値を得る為に、リング摺動部材12とディスク状摺動部材10の相対すべり速度と潤滑油の粘度と面圧を変化させた。 In addition, the experimental conditions by the said friction experiment apparatus were as follows in order to measure the friction coefficient in boundary lubrication, mixed lubrication, and fluid lubrication. The load is 6N to 110N, the speed is 0.06 to 0.6m / sec, the viscosity is 4.6 to 130mm 2 / sec, the oil supply is 0.12cm 3 / min (0.03cm 3 × 4 times / Minutes).
The ring-shaped sliding
Furthermore, the bearing characteristics of boundary lubrication in a sliding state in which an oil film is hard to form and metal contact occurs, fluid lubrication in an oil film formed and sliding state in which metal contact is hard to occur, and mixed lubrication in its transition state. In order to obtain the values, the relative sliding speed of the
開口面積率とは、リング状摺動部材12とディスク状摺動部材10が接触する摺動面138の面積に対する凹部136の開口部分の総面積の割合のことである。摺動部材の摺動面138の一部をレーザー顕微鏡にて取り込んでコンピュータ画像処理を行った。凹部136の開口部と、平坦部137を分別した後に、個々の凹部136の開口部の開口面積の総和を画像処理に用いた摺動面138の全面積で除することで、開口面積率を得ている。尚、測定箇所を変えて数回計測して得られた開口面積率の平均値をその条件での代表値とした。
また、面粗度は触針式の形状測定機で数回計測した結果の平均値を、また凹部136の深さはレーザー顕微鏡で数回測定した結果の平均値を示している。 The opening area ratio is the ratio of the total area of the opening of therecess 136 to the area of the sliding surface 138 where the ring-shaped sliding member 12 and the disk-shaped sliding member 10 contact. A part of the sliding surface 138 of the sliding member was taken in by a laser microscope to perform computer image processing. The opening area ratio is obtained by dividing the sum of the opening areas of the openings of the concave portions 136 and the flat portions 137 and then dividing the sum of the opening areas of the openings of the individual concave portions 136 by the total area of the sliding surface 138 used for image processing. It has gained. In addition, the average value of the opening area ratio obtained by changing a measurement location and measuring several times was made into the representative value in the conditions.
Further, the surface roughness indicates the average value of the results measured several times with a stylus type shape measuring machine, and the depth of therecess 136 indicates the average value of the results measured several times with the laser microscope.
また、面粗度は触針式の形状測定機で数回計測した結果の平均値を、また凹部136の深さはレーザー顕微鏡で数回測定した結果の平均値を示している。 The opening area ratio is the ratio of the total area of the opening of the
Further, the surface roughness indicates the average value of the results measured several times with a stylus type shape measuring machine, and the depth of the
図3は、本発明の実施の形態における摺動面の形態をパラメータとした摩擦係数特性図であり、軸受特性数をx軸に、摩擦係数をy軸に示したものである。
軸受特性数とは、潤滑油の粘度と速度を乗じたものを面圧で除した無次元数で潤滑の状態の指標である。軸受特性数が小さくなるに従って金属面が油膜で隔てられている流体潤滑領域から、油膜が薄くなり金属面の接触が発生する混合潤滑域、更に油膜が非常に少なく金属接触が過多となる境界潤滑領域へと変化する。
図3には、本実施の形態1である条件1(□印)、条件2(△印)、および従来の条件3(◇印)の結果を示している。条件1は、凹部136の開口直径が0.184mm、開口面積率が16%、摺動面138の面粗度がRa0.21、凹部136の深さが1.2μmである。条件2は、凹部136の開口直径が0.176mm、開口面積率が35%、摺動面138の面粗度がRa0.23、凹部136の深さが9.4μmである。条件3は凹み加工を行わず、従来の平滑面であり、摺動面138の面粗度はRa0.2である。 FIG. 3 is a characteristic view of the coefficient of friction with the form of the sliding surface in the embodiment of the present invention as a parameter, and shows the number of bearing characteristics on the x axis and the coefficient of friction on the y axis.
The bearing characteristic number is a non-dimensional number obtained by dividing the product of viscosity and speed of lubricating oil by surface pressure, and is an index of the state of lubrication. From the fluid lubrication area where the metal surface is separated by oil film as the number of bearing characteristics decreases, the oil film becomes thinner and mixed lubrication area where metal surface contact occurs, boundary lubrication where the oil film is very small and metal contact is excessive Change to the area.
FIG. 3 shows the results of the condition 1 (□), the condition 2 (Δ) and the conventional condition 3 (実 施) according to the first embodiment. Incondition 1, the opening diameter of the recess 136 is 0.184 mm, the opening area ratio is 16%, the surface roughness Ra of the sliding surface 138 is 0.21, and the depth of the recess 136 is 1.2 μm. Condition 2 is that the opening diameter of the recess 136 is 0.176 mm, the opening area ratio is 35%, the surface roughness Ra of the sliding surface 138 is 0.23, and the depth of the recess 136 is 9.4 μm. Condition 3 is a conventional smooth surface without concave processing, and the surface roughness of the sliding surface 138 is Ra 0.2.
軸受特性数とは、潤滑油の粘度と速度を乗じたものを面圧で除した無次元数で潤滑の状態の指標である。軸受特性数が小さくなるに従って金属面が油膜で隔てられている流体潤滑領域から、油膜が薄くなり金属面の接触が発生する混合潤滑域、更に油膜が非常に少なく金属接触が過多となる境界潤滑領域へと変化する。
図3には、本実施の形態1である条件1(□印)、条件2(△印)、および従来の条件3(◇印)の結果を示している。条件1は、凹部136の開口直径が0.184mm、開口面積率が16%、摺動面138の面粗度がRa0.21、凹部136の深さが1.2μmである。条件2は、凹部136の開口直径が0.176mm、開口面積率が35%、摺動面138の面粗度がRa0.23、凹部136の深さが9.4μmである。条件3は凹み加工を行わず、従来の平滑面であり、摺動面138の面粗度はRa0.2である。 FIG. 3 is a characteristic view of the coefficient of friction with the form of the sliding surface in the embodiment of the present invention as a parameter, and shows the number of bearing characteristics on the x axis and the coefficient of friction on the y axis.
The bearing characteristic number is a non-dimensional number obtained by dividing the product of viscosity and speed of lubricating oil by surface pressure, and is an index of the state of lubrication. From the fluid lubrication area where the metal surface is separated by oil film as the number of bearing characteristics decreases, the oil film becomes thinner and mixed lubrication area where metal surface contact occurs, boundary lubrication where the oil film is very small and metal contact is excessive Change to the area.
FIG. 3 shows the results of the condition 1 (□), the condition 2 (Δ) and the conventional condition 3 (実 施) according to the first embodiment. In
図3から、摺動条件である荷重、速度、粘度を変更して、軸受特性数を変化させたが、摩擦係数は一本の線上に乗ることが判り、本実験で軸受特性数と摩擦係数の関係を示すことは可能であるといえる。その結果、従来のリング状摺動部材、及びディスク状摺動部材がともに平滑面である条件3(◇印)の場合に比べ、条件1(□印)は軸受特性数が小さい、つまり、境界潤滑から混合潤滑の領域において、摩擦係数が低くなっている。また、条件2(△印)は軸受特性数が大きい、つまり流体潤滑の領域において、摩擦係数が低くなっていることが判る。
この実験結果から、一つの摺動部の中で、軸受特性数つまり負荷状態の分布に適合したディンプルの仕様を選定して摺動面に配設することにより、平滑面に比べて低い摩擦係数でかつその変動や不安定な摺動を抑制するとともに、摺動面138の摩耗状態も緩和することができることが分かる。 From FIG. 3, it was found that the bearing characteristic number was changed by changing the load, speed, and viscosity which are sliding conditions, but the coefficient of friction was on one line, and in this experiment the number of bearing characteristics and the coefficient of friction It is possible to show the relationship of As a result, the number of bearing characteristics is smaller in condition 1 (□ mark) than in the case of condition 3 (mark 従 来 mark) in which both the conventional ring-shaped sliding member and the disk-shaped sliding member are smooth surfaces. The coefficient of friction is low in the area from lubrication to mixed lubrication. Further, it can be seen that thecondition 2 (.DELTA. Mark) indicates that the number of bearing characteristics is large, that is, the coefficient of friction is low in the region of fluid lubrication.
From this experimental result, the coefficient of friction is lower than that of a smooth surface by selecting the dimple specifications that match the bearing characteristic number, that is, the distribution of the loading condition, in one sliding portion and arranging them on the sliding surface. In addition, it is understood that the wear state of the slidingsurface 138 can be alleviated as well as suppressing the fluctuation and unstable sliding.
この実験結果から、一つの摺動部の中で、軸受特性数つまり負荷状態の分布に適合したディンプルの仕様を選定して摺動面に配設することにより、平滑面に比べて低い摩擦係数でかつその変動や不安定な摺動を抑制するとともに、摺動面138の摩耗状態も緩和することができることが分かる。 From FIG. 3, it was found that the bearing characteristic number was changed by changing the load, speed, and viscosity which are sliding conditions, but the coefficient of friction was on one line, and in this experiment the number of bearing characteristics and the coefficient of friction It is possible to show the relationship of As a result, the number of bearing characteristics is smaller in condition 1 (□ mark) than in the case of condition 3 (mark 従 来 mark) in which both the conventional ring-shaped sliding member and the disk-shaped sliding member are smooth surfaces. The coefficient of friction is low in the area from lubrication to mixed lubrication. Further, it can be seen that the
From this experimental result, the coefficient of friction is lower than that of a smooth surface by selecting the dimple specifications that match the bearing characteristic number, that is, the distribution of the loading condition, in one sliding portion and arranging them on the sliding surface. In addition, it is understood that the wear state of the sliding
尚、本発明は様々な装置の種々の摺動部材に適用可能であり、摺動部材の材質や表面性状(初期の面粗度)、運転条件や、潤滑油の供給状態や油性(粘度や油種など)に応じて、適正な凹部136の諸要素を決定することが必要である。
具体例としては、冷凍サイクル用圧縮機の1つであるレシプロ圧縮機の摺動部材が挙げられる。図4にレシプロ圧縮機の横断面図を示す。 The present invention is applicable to various sliding members of various devices, and the material and surface properties (initial surface roughness) of the sliding member, operating conditions, supply state of lubricating oil and oiliness (viscosity and Depending on the oil type, etc., it is necessary to determine the appropriate elements of therecess 136.
As a specific example, a sliding member of a reciprocating compressor, which is one of refrigeration cycle compressors, can be mentioned. FIG. 4 shows a cross-sectional view of the reciprocating compressor.
具体例としては、冷凍サイクル用圧縮機の1つであるレシプロ圧縮機の摺動部材が挙げられる。図4にレシプロ圧縮機の横断面図を示す。 The present invention is applicable to various sliding members of various devices, and the material and surface properties (initial surface roughness) of the sliding member, operating conditions, supply state of lubricating oil and oiliness (viscosity and Depending on the oil type, etc., it is necessary to determine the appropriate elements of the
As a specific example, a sliding member of a reciprocating compressor, which is one of refrigeration cycle compressors, can be mentioned. FIG. 4 shows a cross-sectional view of the reciprocating compressor.
現状のレシプロ圧縮機150の摺動部材としては次のものが一般的である。
(1)シャフト主軸151と主軸受152は片持ち軸受構造であるために、主軸受152の上下端部で片当りが起こる可能性がある。また、どちらの材質も鋳鉄製である。シャフト主軸151は、その表面にリン酸マンガン皮膜処理がなされ、シャフト主軸151の方が主軸受152に比べやや硬度が低い。シャフト主軸151の摺動面及び摺軸受け152の摺動面は、ともに面粗度Ra0.5以下に仕上げられている。
(2)スラスト軸受部153に関して、冷媒の吸入圧縮行程においてクランクシャフトが主軸受152内で傾くことで、シャフト主軸151側のスラスト摺動面154と主軸受152側のスラスト摺動面155の外周側で片当りが起こる可能性があるとともに、平面接触のため油膜圧力が発生し難い。また、シャフト主軸151側のスラスト摺動面154及び主軸受152側のスラスト摺動面155のいずれも鋳鉄製で、主軸側のスラスト摺動面154は一般的にリン酸マンガン皮膜処理がなされ、シャフト主軸151側のスラスト摺動面154の方がやや硬度が低い。スラスト摺動面154、155は、ともに面粗度Ra0.5以下に仕上げられている。
(3)シャフト偏心軸156とコンロッド大端孔157に関して、冷媒の吸入圧縮行程においてコンロッド大端孔157の上下端部で片当りが起こる可能性がある。シャフト偏心軸156が鋳鉄製で、コンロッド158がアルミ合金製であり、シャフト偏心軸156の面及びコンロッド大端孔157の面は、ともに面粗度Ra0.5以下に仕上げられている。
(4)ピストンピン159とコンロッド小端孔160に関して、ピストンピン159がコンロッド小端孔160内で揺動運動するので油膜が一定方向の回転運動に比べて形成され難く、かつ摺動面積が他の摺動部に比べて小さく面圧が高くなる。ピストンピン159がクロム鋼製で、コンロッド158がアルミ合金製である。ピストンピン159の摺動面及びコンロッド小端孔160の摺動面は、ともに面粗度Ra0.5以下に仕上げられている。ピストンピン159は一般的に表面焼入されているかあるいは窒化処理などで表面硬化がなされている。
(5)ピストン161とシリンダボア162に関して、冷媒の吸入圧縮行程においてクランクシャフト163が主軸受152内で傾き、ピストンがレシプロ圧縮機150を横から見て上下方向に傾斜することでピストン161の上下端部で片当りが起こる可能性がある。ピストン161は焼結鉄製で、表面にリン酸マンガン処理がなされている。一方のシリンダボア162は鋳鉄製であり、ピストン161に比べてやや硬度が低い。ピストン161の摺動面及びシリンダボア162の摺動面は、ともに面粗度Ra0.5以下に仕上げられている。 The following is generally used as a sliding member of thepresent reciprocating compressor 150.
(1) The shaft main shaft 151 and themain bearing 152 have a cantilever bearing structure, so that the upper and lower ends of the main bearing 152 may come into contact with one another. Also, both materials are made of cast iron. The shaft main shaft 151 is subjected to a manganese phosphate coating treatment on its surface, and the shaft main shaft 151 is slightly lower in hardness than the main bearing 152. The sliding surface of the shaft main shaft 151 and the sliding surface of the slide bearing 152 are both finished to have a surface roughness Ra of 0.5 or less.
(2) With respect to thethrust bearing portion 153, the crankshaft is inclined within the main bearing 152 in the suction compression stroke of the refrigerant, whereby the thrust sliding surface 154 on the shaft main shaft 151 side and the outer periphery of the thrust sliding surface 155 on the main bearing 152 side One side contact may occur, and oil film pressure is less likely to occur due to planar contact. Further, the thrust sliding surface 154 on the shaft main shaft 151 side and the thrust sliding surface 155 on the main bearing 152 side are both made of cast iron, and the thrust sliding surface 154 on the main shaft side is generally subjected to a manganese phosphate coating treatment The hardness of the thrust sliding surface 154 on the shaft main shaft 151 side is slightly lower. The thrust sliding surfaces 154 and 155 are both finished to have a surface roughness Ra of 0.5 or less.
(3) With respect to the shaft eccentric shaft 156 and the connecting rodlarge end hole 157, a partial contact may occur at the upper and lower ends of the connecting rod large end hole 157 in the suction compression stroke of the refrigerant. The shaft eccentric shaft 156 is made of cast iron, the connecting rod 158 is made of aluminum alloy, and the surface of the shaft eccentric shaft 156 and the surface of the connecting rod large end hole 157 are both finished to have a surface roughness Ra of 0.5 or less.
(4) Thepiston pin 159 swings in the connecting rod small end hole 160 with respect to the piston pin 159 and the connecting rod small end hole 160, so the oil film is difficult to be formed compared to rotational movement in a fixed direction, and the sliding area is other The contact pressure is smaller and smaller than that of the sliding portion. The piston pin 159 is made of chrome steel, and the connecting rod 158 is made of aluminum alloy. The sliding surface of the piston pin 159 and the sliding surface of the connecting rod small end hole 160 are both finished to have a surface roughness Ra of 0.5 or less. The piston pin 159 is generally surface hardened or surface hardened by nitriding or the like.
(5) With respect to the piston 161 and the cylinder bore 162, the crankshaft 163 is inclined within themain bearing 152 in the suction compression stroke of the refrigerant, and the piston is inclined in the vertical direction as viewed from the side of the reciprocating compressor 150 One part may occur in a part. The piston 161 is made of sintered iron, and the surface thereof is treated with manganese phosphate. One cylinder bore 162 is made of cast iron and has a somewhat lower hardness than the piston 161. The sliding surface of the piston 161 and the sliding surface of the cylinder bore 162 are both finished to have a surface roughness Ra of 0.5 or less.
(1)シャフト主軸151と主軸受152は片持ち軸受構造であるために、主軸受152の上下端部で片当りが起こる可能性がある。また、どちらの材質も鋳鉄製である。シャフト主軸151は、その表面にリン酸マンガン皮膜処理がなされ、シャフト主軸151の方が主軸受152に比べやや硬度が低い。シャフト主軸151の摺動面及び摺軸受け152の摺動面は、ともに面粗度Ra0.5以下に仕上げられている。
(2)スラスト軸受部153に関して、冷媒の吸入圧縮行程においてクランクシャフトが主軸受152内で傾くことで、シャフト主軸151側のスラスト摺動面154と主軸受152側のスラスト摺動面155の外周側で片当りが起こる可能性があるとともに、平面接触のため油膜圧力が発生し難い。また、シャフト主軸151側のスラスト摺動面154及び主軸受152側のスラスト摺動面155のいずれも鋳鉄製で、主軸側のスラスト摺動面154は一般的にリン酸マンガン皮膜処理がなされ、シャフト主軸151側のスラスト摺動面154の方がやや硬度が低い。スラスト摺動面154、155は、ともに面粗度Ra0.5以下に仕上げられている。
(3)シャフト偏心軸156とコンロッド大端孔157に関して、冷媒の吸入圧縮行程においてコンロッド大端孔157の上下端部で片当りが起こる可能性がある。シャフト偏心軸156が鋳鉄製で、コンロッド158がアルミ合金製であり、シャフト偏心軸156の面及びコンロッド大端孔157の面は、ともに面粗度Ra0.5以下に仕上げられている。
(4)ピストンピン159とコンロッド小端孔160に関して、ピストンピン159がコンロッド小端孔160内で揺動運動するので油膜が一定方向の回転運動に比べて形成され難く、かつ摺動面積が他の摺動部に比べて小さく面圧が高くなる。ピストンピン159がクロム鋼製で、コンロッド158がアルミ合金製である。ピストンピン159の摺動面及びコンロッド小端孔160の摺動面は、ともに面粗度Ra0.5以下に仕上げられている。ピストンピン159は一般的に表面焼入されているかあるいは窒化処理などで表面硬化がなされている。
(5)ピストン161とシリンダボア162に関して、冷媒の吸入圧縮行程においてクランクシャフト163が主軸受152内で傾き、ピストンがレシプロ圧縮機150を横から見て上下方向に傾斜することでピストン161の上下端部で片当りが起こる可能性がある。ピストン161は焼結鉄製で、表面にリン酸マンガン処理がなされている。一方のシリンダボア162は鋳鉄製であり、ピストン161に比べてやや硬度が低い。ピストン161の摺動面及びシリンダボア162の摺動面は、ともに面粗度Ra0.5以下に仕上げられている。 The following is generally used as a sliding member of the
(1) The shaft main shaft 151 and the
(2) With respect to the
(3) With respect to the shaft eccentric shaft 156 and the connecting rod
(4) The
(5) With respect to the piston 161 and the cylinder bore 162, the crankshaft 163 is inclined within the
以上の摺動部材の組合せにおいて、本発明は、すべての摺動が想定される部位に有効であると考えられる。すなわち、境界潤滑領域、及び混合潤滑領域(摺動部材同士が接触して摺動する)での摺動が想定される部位(運転後の表面状態を仔細に観察することにより判別が可能)には開口面積が少なめで凹部深さが浅目の凹部を、流体潤滑領域(摺動部材は油膜で隔てられた状態で摺動が想定される部位)には開口面積が多目で凹部深さが深目の凹部を配設することが極めて有効であると考える。即ち、片当りし易い部位や比較的面圧が高い部位などに対し、相対する摺動部材に、運転回転数、面圧、実使用粘度などに対応した適正な開口面積率、面粗度、及び深さからなる凹部を設けることで、潤滑状態を改善することができる。また、流体潤滑領域に対応する摺動部材に、運転回転数、面圧、実使用粘度などに対応した適正な開口面積率、面粗度、及び深さからなる凹部を設けることで、油膜によるせん断力を低減し、高い効率と高い信頼性を持つレシプロ圧縮機150を実現させることができる。
In the combination of the above sliding members, the present invention is considered to be effective for all possible sliding parts. That is, in a boundary lubrication area and a part where sliding in a mixed lubrication area (sliding members contact and slide) is assumed (discrimination is possible by observing the surface condition after driving) The recess area has a small opening area and a shallow recess depth, and the opening area is large and the recess depth is large in the fluid lubrication area (the area where sliding is assumed to be separated by the oil film of the sliding member) It is considered extremely effective to arrange a deep recess. That is, an appropriate opening area ratio, surface roughness, or the like corresponding to the operating rotational speed, surface pressure, actual use viscosity, etc., of the sliding members facing each other with respect to parts that easily come into contact with one another or parts that have relatively high surface pressure. The lubrication condition can be improved by providing the recess having the and the depth. In addition, the sliding member corresponding to the fluid lubrication region is provided with a recess having an opening area ratio, surface roughness, and depth corresponding to the operating rotational speed, surface pressure, actual use viscosity, etc. A shear force can be reduced, and a reciprocating compressor 150 with high efficiency and high reliability can be realized.
その他の具体例としては、冷凍サイクル用圧縮機の1つであるロータリー圧縮機の摺動部材が挙げられる。図5にロータリー圧縮機の横断面図を示す。
Another specific example is a sliding member of a rotary compressor which is one of refrigeration cycle compressors. FIG. 5 shows a cross-sectional view of the rotary compressor.
現状のロータリー圧縮機170の摺動部材としては次のものが一般的である。
(1)シャフト主軸171と主軸受172、シャフト副軸173と副軸受174に関して、主軸受172、副軸受174の端部にて片当りが起こり易い。シャフト主軸171とシャフト副軸173は一体成型であり鋳鉄製で、シャフト主軸171の摺動面及びシャフト副軸173の摺動面にはリン酸マンガン皮膜処理がなされている。一方の主軸受172、副軸受174は焼結鉄製であり、シャフト主軸171、シャフト副軸173に比べて硬度が低い。主軸受172の摺動面及び副軸受174の摺動面は、ともに面粗度Ra0.5以下に仕上げられている。
(2)ベーン側面175とシリンダベーン溝176については往復動なので油膜圧力が発生し難い。ベーン側面175は合金鋼製で、シリンダベーン溝176は鋳鉄製である。ベーン側面175は面粗度Ra0.5以下に、シリンダベーン溝176はRa1.0以下に仕上げられている。
(3)ベーン先端177とローラ178については線接触摺動で面圧が極めて高くなる。ベーン先端177は合金鋼製で、その摺動面(先端)にはPVD、あるいはCVDによるセラミックス皮膜が形成され硬質化されている。一方のローラ178は鋳鉄製である。ベーン先端177の摺動面及びローラ178の摺動面は、ともに面粗度Ra0.5以下に仕上げられている。 The following is generally used as a sliding member of the currentrotary compressor 170.
(1) With respect to the shaftmain shaft 171 and the main bearing 172, and the shaft subshaft 173 and the subbearing 174, one end contact of the end of the main bearing 172 and the subbearing 174 is likely to occur. The shaft main shaft 171 and the shaft sub-shaft 173 are integrally formed and made of cast iron, and the sliding surface of the shaft main shaft 171 and the sliding surface of the shaft sub-shaft 173 are treated with a manganese phosphate coating. One main bearing 172 and the secondary bearing 174 are made of sintered iron and have lower hardness than the shaft main shaft 171 and the shaft secondary shaft 173. The sliding surface of the main bearing 172 and the sliding surface of the sub bearing 174 are both finished to have a surface roughness Ra of 0.5 or less.
(2) Since thevane side surface 175 and the cylinder vane groove 176 reciprocate, it is difficult for oil film pressure to be generated. The vane side surface 175 is made of alloy steel, and the cylinder vane groove 176 is made of cast iron. The vane side surface 175 is finished to a surface roughness Ra of 0.5 or less, and the cylinder vane groove 176 is finished to Ra1 or less.
(3) The surface pressure of thevane tip 177 and the roller 178 becomes extremely high due to the line contact sliding. The vane tip 177 is made of alloy steel, and the sliding surface (tip) is hardened by forming a ceramic film by PVD or CVD. One roller 178 is made of cast iron. The sliding surface of the vane tip 177 and the sliding surface of the roller 178 are both finished to have a surface roughness Ra of 0.5 or less.
(1)シャフト主軸171と主軸受172、シャフト副軸173と副軸受174に関して、主軸受172、副軸受174の端部にて片当りが起こり易い。シャフト主軸171とシャフト副軸173は一体成型であり鋳鉄製で、シャフト主軸171の摺動面及びシャフト副軸173の摺動面にはリン酸マンガン皮膜処理がなされている。一方の主軸受172、副軸受174は焼結鉄製であり、シャフト主軸171、シャフト副軸173に比べて硬度が低い。主軸受172の摺動面及び副軸受174の摺動面は、ともに面粗度Ra0.5以下に仕上げられている。
(2)ベーン側面175とシリンダベーン溝176については往復動なので油膜圧力が発生し難い。ベーン側面175は合金鋼製で、シリンダベーン溝176は鋳鉄製である。ベーン側面175は面粗度Ra0.5以下に、シリンダベーン溝176はRa1.0以下に仕上げられている。
(3)ベーン先端177とローラ178については線接触摺動で面圧が極めて高くなる。ベーン先端177は合金鋼製で、その摺動面(先端)にはPVD、あるいはCVDによるセラミックス皮膜が形成され硬質化されている。一方のローラ178は鋳鉄製である。ベーン先端177の摺動面及びローラ178の摺動面は、ともに面粗度Ra0.5以下に仕上げられている。 The following is generally used as a sliding member of the current
(1) With respect to the shaft
(2) Since the
(3) The surface pressure of the
以上の摺動部材の組合せにおいて、本発明は、すべての摺動が想定される部位に有効であると考えられる。すなわち、境界潤滑領域、及び混合潤滑領域(摺動部材同士が接触して摺動する)での摺動が想定される部位(運転後の表面状態を仔細に観察することにより判別が可能)には開口面積が少なめで凹部深さが浅目の凹部を、流体潤滑領域(摺動部材は油膜で隔てられた状態で摺動が想定される部位)には開口面積が多目で凹部深さが深目の凹部を配設することが極めて有効であると考える。即ち、片当りし易い部位や潤滑状態が厳しい部位などに対し、相対する摺動部材に、運転回転数、面圧、実使用粘度などに対応した適正な開口面積率、面粗度、及び深さからなる凹部を設けることで、潤滑状態を改善することができる。また、流体潤滑領域に対応する摺動部材に、運転回転数、面圧、実使用粘度などに対応した適正な開口面積率、面粗度、及び深さからなる凹部を設けることで、油膜によるせん断力を低減し、高い効率と高い信頼性を持つロータリー圧縮機170を実現することができる。
In the combination of the above sliding members, the present invention is considered to be effective for all possible sliding parts. That is, in a boundary lubrication area and a part where sliding in a mixed lubrication area (sliding members contact and slide) is assumed (discrimination is possible by observing the surface condition after driving) The recess area has a small opening area and a shallow recess depth, and the opening area is large and the recess depth is large in the fluid lubrication area (the area where sliding is assumed to be separated by the oil film of the sliding member) It is considered extremely effective to arrange a deep recess. That is, the appropriate opening area ratio, the surface roughness, and the depth corresponding to the operating rotation speed, the surface pressure, the actual use viscosity, etc., on the opposite sliding member, with respect to the parts that easily come into contact The lubrication can be improved by providing the recess having the taper. In addition, the sliding member corresponding to the fluid lubrication region is provided with a recess having an opening area ratio, surface roughness, and depth corresponding to the operating rotational speed, surface pressure, actual use viscosity, etc. A shear force can be reduced, and a rotary compressor 170 with high efficiency and high reliability can be realized.
さらに、その他の具体例としては、冷凍サイクル用圧縮機の1つであるスクロール圧縮機の摺動部材がある。図6にスクロール圧縮機の横断面図を示す。
Furthermore, as another specific example, there is a sliding member of a scroll compressor which is one of compressors for a refrigeration cycle. FIG. 6 shows a cross-sectional view of the scroll compressor.
現状のスクロール圧縮機180の摺動部材としては次のものが一般的である。
(1)シャフト主軸181と主軸受182、シャフト偏心軸183と偏心軸受184、シャフト副軸185と副軸受186については構造上、主軸受182、偏心軸受184、副軸受186の上下端部で片当りが起こり易い。シャフト主軸181、シャフト偏心軸183、シャフト副軸185はいずれも表面硬化された合金鋼製である。一方の主軸受182、偏心軸受184、副軸受186はいずれも裏金を金属とした樹脂とカーボンの複合材である。シャフト主軸181の摺動面、シャフト偏心軸183の摺動面、及びシャフト副軸186の摺動面は、いずれも面粗度Ra0.5以下に仕上げられている。
(2)固定スクロール188と、主軸受182側から圧縮ガスで固定スクロール188に押し付けられている旋回スクロール189との間に形成されるスラスト軸受面190については平面接触のために油膜圧力が比較的発生し難い。また、スクロール圧縮機の特徴で外周部は低圧、内周部は高圧となるため、スラスト軸受面190は、荷重が変化しやすい摺動面である。固定スクロール188が鋳鉄製で、旋回スクロール189はアルミニウム合金製である。固定スクロール188の摺動面及び旋回スクロール189の摺動面は、とも面粗度Ra0.5以下に仕上げられている。 The following is generally used as a sliding member of the present scroll compressor 180.
(1) The shaft main shaft 181 and the main bearing 182, the shaft eccentric shaft 183 and the eccentric bearing 184, and the shaft sub shaft 185 and the sub bearing 186 are structurally at the upper and lower ends of the main bearing 182, the eccentric bearing 184 and the sub bearing 186 Hit is easy to happen. The shaft main shaft 181, the shaft eccentric shaft 183, and the shaft countershaft 185 are all made of surface hardened alloy steel. The one main bearing 182, the eccentric bearing 184, and the sub bearing 186 are all composites of resin and carbon with the metal back metal. The sliding surface of the shaft main shaft 181, the sliding surface of the shaft eccentric shaft 183, and the sliding surface of the shaft countershaft 186 are all finished to have a surface roughness Ra of 0.5 or less.
(2) The oil film pressure of thethrust bearing surface 190 formed between the fixed scroll 188 and the orbiting scroll 189 pressed against the fixed scroll 188 by the compressed gas from the main bearing 182 side is relatively flat due to flat contact. It is hard to occur. Further, since the outer peripheral portion is a low pressure and the inner peripheral portion is a high pressure, which is characteristic of the scroll compressor, the thrust bearing surface 190 is a sliding surface on which the load is easily changed. The fixed scroll 188 is made of cast iron, and the orbiting scroll 189 is made of aluminum alloy. The sliding surface of the fixed scroll 188 and the sliding surface of the orbiting scroll 189 are both finished to have a surface roughness Ra of 0.5 or less.
(1)シャフト主軸181と主軸受182、シャフト偏心軸183と偏心軸受184、シャフト副軸185と副軸受186については構造上、主軸受182、偏心軸受184、副軸受186の上下端部で片当りが起こり易い。シャフト主軸181、シャフト偏心軸183、シャフト副軸185はいずれも表面硬化された合金鋼製である。一方の主軸受182、偏心軸受184、副軸受186はいずれも裏金を金属とした樹脂とカーボンの複合材である。シャフト主軸181の摺動面、シャフト偏心軸183の摺動面、及びシャフト副軸186の摺動面は、いずれも面粗度Ra0.5以下に仕上げられている。
(2)固定スクロール188と、主軸受182側から圧縮ガスで固定スクロール188に押し付けられている旋回スクロール189との間に形成されるスラスト軸受面190については平面接触のために油膜圧力が比較的発生し難い。また、スクロール圧縮機の特徴で外周部は低圧、内周部は高圧となるため、スラスト軸受面190は、荷重が変化しやすい摺動面である。固定スクロール188が鋳鉄製で、旋回スクロール189はアルミニウム合金製である。固定スクロール188の摺動面及び旋回スクロール189の摺動面は、とも面粗度Ra0.5以下に仕上げられている。 The following is generally used as a sliding member of the present scroll compressor 180.
(1) The shaft main shaft 181 and the main bearing 182, the shaft eccentric shaft 183 and the eccentric bearing 184, and the shaft sub shaft 185 and the sub bearing 186 are structurally at the upper and lower ends of the main bearing 182, the eccentric bearing 184 and the sub bearing 186 Hit is easy to happen. The shaft main shaft 181, the shaft eccentric shaft 183, and the shaft countershaft 185 are all made of surface hardened alloy steel. The one main bearing 182, the eccentric bearing 184, and the sub bearing 186 are all composites of resin and carbon with the metal back metal. The sliding surface of the shaft main shaft 181, the sliding surface of the shaft eccentric shaft 183, and the sliding surface of the shaft countershaft 186 are all finished to have a surface roughness Ra of 0.5 or less.
(2) The oil film pressure of the
以上の摺動部材の組合せにおいて、本発明は、すべての摺動が想定される部位に有効であると考えられる。すなわち、境界潤滑領域、及び混合潤滑領域(摺動部材同士が接触して摺動する)での摺動が想定される部位(運転後の表面状態を仔細に観察することにより判別が可能)には開口面積が少なめで凹部深さが浅目の凹部を、流体潤滑領域(摺動部材は油膜で隔てられた状態で摺動が想定される部位)には開口面積が多目で凹部深さが深目の凹部を配設することが極めて有効であると考える。即ち、片当りし易い部位や潤滑状態が厳しい領域などに対し、相対する摺動部材に、運転回転数、面圧、実使用粘度などに対応した適正な開口面積率、面粗度、及び深さからなる凹部を設けることで、潤滑状態を改善することができる。また、流体潤滑領域に対応する摺動部材に、運転回転数、面圧、実使用粘度などに対応した適正な開口面積率、面粗度、及び深さからなる凹部を設けることで、油膜によるせん断力を低減し、高い効率と高い信頼性を持つスクロール圧縮機180の高効率、信頼性化を実現させることができる。
In the combination of the above sliding members, the present invention is considered to be effective for all possible sliding parts. That is, in a boundary lubrication area and a part where sliding in a mixed lubrication area (sliding members contact and slide) is assumed (discrimination is possible by observing the surface condition after driving) The recess area has a small opening area and a shallow recess depth, and the opening area is large and the recess depth is large in the fluid lubrication area (the area where sliding is assumed to be separated by the oil film of the sliding member) It is considered extremely effective to arrange a deep recess. That is, an appropriate open area ratio, surface roughness, and depth corresponding to the operating rotational speed, surface pressure, actual use viscosity, etc., of the sliding members facing each other with respect to a portion that easily comes into contact or an area where lubrication is severe. The lubrication can be improved by providing the recess having the taper. In addition, the sliding member corresponding to the fluid lubrication region is provided with a recess having an opening area ratio, surface roughness, and depth corresponding to the operating rotational speed, surface pressure, actual use viscosity, etc. The shear force can be reduced, and high efficiency and high reliability of the scroll compressor 180 having high efficiency and high reliability can be realized.
図7の運転後の固定スクロール188のスラスト軸受面190の観察から、油膜が薄く金属接触が起こっている境界潤滑及び混合潤滑の領域は図8に示すようなインボリュートの内周側191であり、油膜ができやすく金属接触は起こりにくい(起こってない)流体潤滑の領域は図9に示すインボリュートの外周側192となっていた。
From the observation of the thrust bearing surface 190 of the fixed scroll 188 after the operation of FIG. 7, the region of boundary lubrication and mixed lubrication where the oil film is thin and metal contact is occurring is the inner peripheral side 191 of the involute as shown in FIG. The area of fluid lubrication where oil film is likely to occur and metal contact is not likely to occur (is not occurring) is the outer peripheral side 192 of the involute shown in FIG.
具体的には、境界潤滑及び混合潤滑の領域では、油膜が薄く、金属接触が起こっている。従って、境界潤滑及び混合潤滑の領域では、粗さ(凸部)が磨耗し、磨耗によって発生する粉によって傷が発生するため、鏡面磨耗を観察することができる。この磨耗によって発生する粉は相手材を削るとともに相手材に凝着し、凝着した粉が一気に引き剥がされると大きな傷ができる。鏡面磨耗になった場合には、油溜りがなくなり油膜ができにくくなることにより凝着が発生しやすくなる。そして、最終的には大きな傷を発生させ、磨耗が進行し、摺動部材の信頼性を大きく損なうこととなる。鋳鉄製の固定スクロールとアルミニウム合金製の可動スクロールの場合、鋳鉄に凝着するアルミニウム合金の磨耗によって発生する粉が引き剥がされる時に大きな傷が発生している場合が有った。流体潤滑の領域は、油膜が厚く金属接触が発生していない為、摺動痕が付いていない。すなわち、加工痕が残ったままの初期の表面状態であり、面粗さも初期の状態である。これらの観点から運転後の圧縮機部品の表面を注意深く観察することにより、境界潤滑及び混合潤滑領域(摺動部材同士が接触して摺動する)での摺動が想定される部位と流体潤滑領域(摺動部材は油膜で隔てられた状態で摺動する)が想定される部位とを分けることができ、それぞれの潤滑状態に応じた凹部仕様を選定することが必要である。
Specifically, in the area of boundary lubrication and mixed lubrication, the oil film is thin and metal contact occurs. Accordingly, in the area of boundary lubrication and mixed lubrication, it is possible to observe specular wear because the roughness (convex portion) is worn and the powder generated by the wear causes scratches. The powder generated by this abrasion scrapes the mating material and adheres to the mating material, and if the coagulated powder is pulled away at a stretch, a large scratch will occur. In the case of mirror surface wear, the accumulation of oil is eliminated and the oil film is less likely to be formed, so that adhesion is likely to occur. Finally, a large scratch is generated, wear progresses, and the reliability of the sliding member is greatly impaired. In the case of a fixed cast iron scroll and a movable scroll made of aluminum alloy, when the powder generated by the wear of the aluminum alloy adhering to the cast iron was torn off, a large scratch might have occurred. In the area of fluid lubrication, the oil film is thick and metal contact is not generated, so no sliding marks are formed. That is, it is an initial surface state with remaining processing marks, and the surface roughness is also in the initial state. From these points of view, by carefully observing the surface of the compressor part after operation, fluid lubrication and a part where sliding in a boundary lubrication and mixed lubrication area (sliding members contact and slide) is assumed A region (sliding member slides in a state of being separated by an oil film) can be separated from the assumed portion, and it is necessary to select a recess specification according to each lubrication state.
この固定スクロール188のスラスト軸受面190の内周側191には、図3で境界潤滑から混合潤滑領域で摩擦係数低減効果が有った直径0.184×深さ1.2μm×開口面積率16%の略円形状のディンプルを加工した。スラスト軸受面190の外周側192には、図3で流体潤滑領域で摩擦係数低減効果が有った直径0.176×深さ9.4μm×開口面積率35%の略円形形状のディンプルを加工した。冷媒雰囲気での模擬運転および実機運転で確認したところ、0.5~1%程度の効率向上が認められた。また、運転後、内周側191の擦り傷の程度がディンプルのない状態に比べて軽くなっており、潤滑性も向上していることが想定され、信頼性が上がっていると言える。
また、運転後の凹部内の観察から、磨耗によって発生する微小な粉が確認されたことにより、ディンプルは磨耗によって発生した粉の捕捉にも効果を発揮していると考えられる。
この様に、摺動面の負荷の状態により適切なディンプルを設けることにより、性能と信頼性が高いスクロール圧縮機を実現することができる。 On the innerperipheral side 191 of the thrust bearing surface 190 of this fixed scroll 188, the diameter 0.184 × depth 1.2 μm depth × opening area ratio 16 having the effect of reducing the friction coefficient in the mixed lubrication region from the boundary lubrication in FIG. % Of a substantially circular dimple was processed. On the outer peripheral side 192 of the thrust bearing surface 190, a substantially circular dimple having a diameter of 0.176 × 9.4 μm in depth × 35% of open area ratio having the effect of reducing the friction coefficient in the fluid lubrication region in FIG. 3 is processed did. As a result of confirming by the simulated operation and the actual device operation in the refrigerant atmosphere, the efficiency improvement of about 0.5 to 1% was recognized. In addition, after operation, the degree of abrasion on the inner circumferential side 191 is lighter than in the state without dimples, and it can be said that the lubricity is also improved, and the reliability is improved.
In addition, it is considered that the dimples are also effective in capturing the powder generated by the wear, as the minute powder generated by the wear is confirmed from the observation in the concave portion after the operation.
As described above, by providing appropriate dimples according to the load state of the sliding surface, it is possible to realize a scroll compressor having high performance and reliability.
また、運転後の凹部内の観察から、磨耗によって発生する微小な粉が確認されたことにより、ディンプルは磨耗によって発生した粉の捕捉にも効果を発揮していると考えられる。
この様に、摺動面の負荷の状態により適切なディンプルを設けることにより、性能と信頼性が高いスクロール圧縮機を実現することができる。 On the inner
In addition, it is considered that the dimples are also effective in capturing the powder generated by the wear, as the minute powder generated by the wear is confirmed from the observation in the concave portion after the operation.
As described above, by providing appropriate dimples according to the load state of the sliding surface, it is possible to realize a scroll compressor having high performance and reliability.
本発明の摺動部材によれば、互いの摺動面が摺動する2つの摺動部材を有し、少なくとも一方の摺動面において、比較的潤滑状態が厳しい領域では開口面積が少なめで凹部深さが浅目の凹部を設ける。これにより摺動面上の平坦部にてその荷重を面で受け止めるとともに、凹部に保持された潤滑油が平坦部に滲み出ることで、より過酷な摺動条件の場合であっても摩擦損失や摩耗を低減することができる。
これに対し、比較的潤滑状態が厳しくない領域では開口面積が多目で凹部深さが深目の凹部を設ける。これにより、平滑面の面積を減少することができ、潤滑油の粘性抵抗が低くなるとともに凹部に保持された潤滑油が平坦部に滲み出ることで摩擦損失や摩耗を低減できるので、従来の凹部を設けた摺動部材より摩擦損失や摩耗を低減することができる。 According to the sliding member of the present invention, the sliding member has two sliding members on which the sliding surfaces slide with each other, and at least one of the sliding surfaces has a smaller opening area and a recessed portion in a region where the lubrication condition is relatively severe. A shallow recess is provided. As a result, the load is received by the flat portion on the sliding surface, and the lubricating oil held in the concave portion exudes to the flat portion, so that friction loss and the like can be obtained even under more severe sliding conditions. Wear can be reduced.
On the other hand, in the region where the lubrication condition is not so severe, the opening area is large and the recess depth is deep. As a result, the area of the smooth surface can be reduced, and friction loss and wear can be reduced by the viscosity resistance of the lubricating oil becoming low and the lubricating oil held in the concave part permeating out to the flat part. The friction loss and the wear can be reduced more than the sliding member provided with.
これに対し、比較的潤滑状態が厳しくない領域では開口面積が多目で凹部深さが深目の凹部を設ける。これにより、平滑面の面積を減少することができ、潤滑油の粘性抵抗が低くなるとともに凹部に保持された潤滑油が平坦部に滲み出ることで摩擦損失や摩耗を低減できるので、従来の凹部を設けた摺動部材より摩擦損失や摩耗を低減することができる。 According to the sliding member of the present invention, the sliding member has two sliding members on which the sliding surfaces slide with each other, and at least one of the sliding surfaces has a smaller opening area and a recessed portion in a region where the lubrication condition is relatively severe. A shallow recess is provided. As a result, the load is received by the flat portion on the sliding surface, and the lubricating oil held in the concave portion exudes to the flat portion, so that friction loss and the like can be obtained even under more severe sliding conditions. Wear can be reduced.
On the other hand, in the region where the lubrication condition is not so severe, the opening area is large and the recess depth is deep. As a result, the area of the smooth surface can be reduced, and friction loss and wear can be reduced by the viscosity resistance of the lubricating oil becoming low and the lubricating oil held in the concave part permeating out to the flat part. The friction loss and the wear can be reduced more than the sliding member provided with.
すなわち、摺動部材の摺動面に単に同じ凹部を多数設けるのではなく、摺動条件(荷重、潤滑油粘度、速度)により、潤滑状態が厳しい領域とそうでない領域に応じて、凹部の仕様、即ち凹部開口部の大きさ、凹部の深さ、及び摺動部材の摺動面に対する開口部の占める割合を最適に設定して凹部を配設する。これにより、摩耗を抑制して信頼性を更に高める作用を行う領域と、摩擦損失、即ち流体粘性損失を更に減らす作用を行う領域を摺動部材の摺動面に併せ持たせ、効果的に摩擦損失や摩耗を低減し、信頼性の高い摺動部材を提供することができる。
That is, rather than simply providing a large number of the same recesses on the sliding surface of the sliding member, depending on the sliding condition (load, lubricating oil viscosity, speed), the specification of the recess depending on the area where lubrication is severe and not That is, the recess is disposed by optimally setting the size of the recess opening, the depth of the recess, and the ratio of the opening to the sliding surface of the sliding member. Thus, the sliding surface of the sliding member has an area for suppressing wear and further enhancing reliability, and an area for further reducing friction loss, that is, fluid viscosity loss, and the friction is effectively reduced. Loss and wear can be reduced, and a reliable sliding member can be provided.
本発明は摺動部材が用いられている様々な装置、すなわち冷凍サイクル用圧縮機を含む様々な技術分野の各種装置に利用可能である。
The present invention is applicable to various devices in which the sliding member is used, ie, various devices in various technical fields including compressors for refrigeration cycles.
Claims (5)
- 互いの摺動面を摺動する2つの摺動部材を有し、少なくとも一方の前記摺動面に、ディンプル状の複数の凹部を設け、前記凹部の形状又は前記凹部による開口面積率が領域により異なることを特徴とする摺動部材。 It has two sliding members that slide on each other's sliding surface, and at least one of the sliding surfaces is provided with a plurality of dimple-shaped recesses, and the shape of the recesses or the opening area ratio by the recesses is a region Sliding member characterized in that it differs.
- 前記領域によって異なる前記凹部が、開口寸法及び凹部深さの少なくとも一方の形状が異なることを特徴とする請求項1に記載の摺動部材。 The sliding member according to claim 1, wherein the recess different depending on the region has a shape different from at least one of an opening size and a recess depth.
- 前記領域として、第1の領域と第2の領域とを有し、
前記第1の領域が、前記第2の領域よりも潤滑条件が厳しい場合に、
前記第1の領域に形成される前記凹部の前記凹部深さを、前記第2の領域に形成される前記凹部の前記凹部深さよりも浅くし、
前記第1の領域における前記開口面積率を、前記第2の領域における前記開口面積率よりも小さくしたことを特徴とする請求項1又は請求項2に記載の摺動部材。 The area includes a first area and a second area,
In the case where the first region is under stricter lubrication conditions than the second region,
Making the recess depth of the recess formed in the first region shallower than the recess depth of the recess formed in the second region,
The sliding member according to claim 1 or 2, wherein the opening area ratio in the first region is smaller than the opening area ratio in the second region. - 前記凹部の開口面が略円形であることを特徴とする請求項1から請求項3のいずれかに記載の摺動部材。 The sliding member according to any one of claims 1 to 3, wherein the opening surface of the recess is substantially circular.
- 前記摺動部材が、レシプロ圧縮機、ロータリー圧縮機、又はスクロール圧縮機に用いられる部材であることを特徴とする請求項1から請求項4のいずれかに記載の摺動部材。 The said sliding member is a member used for a reciprocating compressor, a rotary compressor, or a scroll compressor, The sliding member in any one of the Claims 1-4 characterized by the above-mentioned.
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CN103635705B (en) | 2017-03-01 |
CN103635705A (en) | 2014-03-12 |
JPWO2013005394A1 (en) | 2015-02-23 |
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