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WO2016072305A1 - Palier lisse rotatif - Google Patents

Palier lisse rotatif Download PDF

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Publication number
WO2016072305A1
WO2016072305A1 PCT/JP2015/080066 JP2015080066W WO2016072305A1 WO 2016072305 A1 WO2016072305 A1 WO 2016072305A1 JP 2015080066 W JP2015080066 W JP 2015080066W WO 2016072305 A1 WO2016072305 A1 WO 2016072305A1
Authority
WO
WIPO (PCT)
Prior art keywords
shaft
bearing
sliding
recesses
concave portion
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Ceased
Application number
PCT/JP2015/080066
Other languages
English (en)
Japanese (ja)
Inventor
樋口　毅
大祐 鶴丸
和彦 高嶋
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Nissan Motor Co Ltd
Original Assignee
Nissan Motor Co Ltd
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Nissan Motor Co Ltd filed Critical Nissan Motor Co Ltd
Publication of WO2016072305A1 publication Critical patent/WO2016072305A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C3/00—Shafts; Axles; Cranks; Eccentrics
    • F16C3/04—Crankshafts, eccentric-shafts; Cranks, eccentrics
    • F16C3/06—Crankshafts
    • F16C3/14—Features relating 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
    • F16C17/00—Sliding-contact bearings for exclusively rotary movement
    • F16C17/02—Sliding-contact bearings for exclusively rotary movement for radial 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
    • F16C9/00—Bearings for crankshafts or connecting-rods; Attachment of connecting-rods
    • F16C9/02—Crankshaft bearings

Definitions

  • the present invention relates to a rotary slide bearing, and more particularly to a rotary slide bearing that achieves both friction reduction and seizure resistance.
  • lubricating oil is supplied between the sliding surfaces, and a continuous lubricating oil film larger than the surface roughness of the sliding member surface is formed, so that the sliding surface wears out. Prevents seizure.
  • the recesses act as an oil pool, and sliding causes pressure fluctuations in the lubricating oil layer, resulting in sliding characteristics like a bearing. It is done. That is, in the distribution of the oil pressure of the lubricating oil layer in the sliding state, the oil pressure is lowered inside the recess, the oil pressure is increased at the edge of the recess, and the interval between the members is expanded.
  • the distribution of oil pressure between the two sliding members is determined by the shape and dimensions of the oil pool, and the presence of many oil pools enables high-lubrication even with a small amount of low-viscosity lubricating oil. Can be improved.
  • the lubricating oil film becomes thick and the oil film is difficult to break and wear and seizure can be prevented, but the internal friction of the lubricating oil increases and friction loss increases.
  • the oil film is made as thin as possible while preventing the occurrence of oil film breakage under all conditions, and the shaft and bearing are in direct contact. It is necessary to avoid this, and setting the recess shape is extremely difficult.
  • Japanese Patent No. 4269726 of Patent Document 1 discloses a sliding member in which a hard carbon film is provided on a sliding surface, a shallow concave portion is provided at a shaft end portion, and a deep concave portion is provided at a central portion of the shaft. Has been.
  • Japanese Patent Publication No. 2011-506855 of Patent Document 2 discloses that the surface roughness of the bearing is small even when the surface roughness of the shaft is small and the bearing is not “run-in” or “familiarization”. It is disclosed that the sliding resistance can be reduced by setting the thickness to a predetermined roughness or less.
  • Patent Document 1 and Patent Document 2 can reduce the frictional force in a situation where the sliding bearing rotates stably and generates an oil film pressure.
  • the load received by the shaft has increased with the increase in engine output, and a large load has been applied in the event of an extreme decrease in viscosity due to temperature rise or a decrease in the amount of lubricant supplied due to operating conditions.
  • the present invention has been made in view of such problems of the prior art, and the object of the present invention is to stably reduce friction under any operating condition by suppressing the frequency of oil film breakage.
  • the purpose is to provide a rotating slide bearing that can achieve both seizure resistance and seizure resistance.
  • the present inventor has found that the above object can be achieved by setting the depth of the concave portion provided on the shaft surface within a desired range, and to complete the present invention. It came.
  • the depth of the concave portion provided on the shaft surface is set within a desired range.
  • FIG. 1 is a cross-sectional view illustrating an example of a section cut in a direction perpendicular to the axial direction
  • FIG. 1B is a schematic diagram illustrating an example of a sliding surface of the shaft.
  • the shaft 2 and the bearing 3 are in sliding contact with each other in the presence of the lubricating oil 4, and a large number of recesses 21 are regularly formed on the sliding surface of the shaft 2.
  • the distribution state of the recesses in a certain unit area is the same as the distribution state of the recesses in another unit area, and the recesses may not be formed at equal intervals.
  • the number of recesses 21 formed on the shaft surface has a depth range of 0.5 ⁇ m to 15 ⁇ m, and more preferably 1.5 to 15 ⁇ m.
  • the pressure distribution of the lubricating oil film on the sliding surface is such that the oil pressure is low inside the recess and the oil pressure is high at the edge of the recess. If there is a recess having a depth of less than 0.5 ⁇ m, the amount of oil retention is not sufficient, and a pressure difference is hardly generated, and therefore an effect of increasing the oil film thickness is hardly expected.
  • the oil retention increases as the depth of the recess increases, but if there is a recess exceeding 15 ⁇ m, local pressure fluctuations increase during high surface pressure and high speed operation, and the oil pressure is extremely high inside the recess. However, microscopically, it becomes difficult to form an oil film, and seizure resistance is reduced.
  • the average depth of the many recesses 21 is 1.5 ⁇ m or more and 15 ⁇ m or less, and preferably 3 ⁇ m or more and 15 ⁇ m or less. When the average depth is less than 1.5 ⁇ m, the amount of oil retention is small and the frequency of oil film breakage increases.
  • the depth of the concave portion can be measured by, for example, a non-contact three-dimensional white light phase modulation interference method using a three-dimensional surface structure analysis microscope.
  • the shaft is elastically deformed when subjected to a large load, for example, when the lubricating oil on the sliding surface is depleted during low speed operation, secondary supply of the lubricating oil is performed from the recess. Burn-in is prevented.
  • the shaft of the present invention preferably has a surface hardness (Rockwell hardness) of 45HRc or more and 65HRc or less.
  • a surface hardness Rockwell hardness
  • the hardness HRc indicates the C scale of Rockwell hardness defined in JISZ2245.
  • the surface roughness (Ra) of portions other than the recesses is 0.10 ⁇ m or less. Locations other than the recesses are locations that are easy to contact with the bearing, and by making the surface roughness (Ra) within this range, contact with the bearing can be suppressed even when the oil film thickness is reduced, and friction The loss reduction effect is brought about.
  • the shape of the opening of the concave portion on the shaft surface is rectangular or elliptical, and it is preferable that the long side direction of the rectangular shape or the major axis direction of the elliptical shape is perpendicular to the sliding direction. Since the long side direction or the long diameter direction is orthogonal to the slip direction, a portion having a high hydraulic pressure can be formed in a wide range, and sliding characteristics like a bearing can be obtained to improve seizure resistance.
  • the area ratio of the opening to the shaft surface is preferably 1% or more and 10% or less. By setting it as this range, sufficient oil retention property is ensured, a flat part area is secured, load capacity against seizure resistance is maintained, and an effect due to the formation of the recess can be exhibited.
  • the area ratio can be calculated, for example, by subjecting a surface observation photograph to image processing.
  • the length of the rectangle or ellipse in the short side / minor axis direction is as short as possible. Specifically, although it depends on the viscosity of the lubricating oil to be used, it is preferably 50 ⁇ m or more and 150 ⁇ m or less, and more preferably 50 ⁇ m or more and 120 ⁇ m or less. By setting it in this range, the concave portion density on the shaft surface can be maintained without increasing the processing cost.
  • the length in the long side / major axis direction is preferably 200 ⁇ m or more and 500 ⁇ m or less. By setting it as this range, the space
  • the concave portion of the present invention can be formed by pressing a convex tool against the shaft surface and transferring the shape (for example, Japanese Patent Application Laid-Open No. 2004-237406, Japanese Patent Application Laid-Open No. 2002-361351).
  • the shape and quantity of the recesses are uniquely determined by the shape of the tool, and the depth is determined by the indentation load or the height of the tool.
  • the concave portions are not necessarily formed by this method.
  • the concave portions are formed by a method of irradiating laser light or a method of projecting hard particles after preparing an appropriate mask (Japanese Patent Laid-Open No. 2003-13710). Also good.
  • the height of the protrusions is preferably suppressed to a height that does not exceed the unevenness of the surface roughness (approximately 0.1 ⁇ m or less).
  • the above bearing has a bearing strength that supports a large load consisting of the explosion force in the cylinder and the inertial force of the moving part, and from the disturbance factors that inhibit the movement of the crankshaft rotating at high speed, the crankshaft Or it protects the engine.
  • an overlay having a thickness of several microns that captures adaptability such as conformability may be formed on the surface of the bearing alloy that supports the load.
  • soft metals such as aluminum, copper, lead, tin, bismuth, and silver
  • engineering plastics such as polyamideimide
  • these materials include PTFE, graphite, molybdenum, etc. It is also possible to add various materials.
  • the surface roughness (Ra) of the bearing is preferably 0.15 ⁇ m or less. By setting it within this range, seizure resistance can be improved.
  • a concave portion may be provided on the bearing surface.
  • the surface of the bearing is formed of a soft material having adaptability such as conformability. When forming the film with high accuracy, the processing may take time.
  • the rotary sliding bearing of the present invention is suitably used for a crankshaft bearing of an automobile engine.
  • Example 1 The surface of columnar SV40C steel (S40C steel defined in JIS G4051 with a small amount of vanadium (V) added) was quenched to a surface hardness of 58HRc. A cylindrical tool having convex portions formed in a line along the circumference was prepared, and the convex shape of the tool was transferred to the surface of the steel material to form a rectangular concave portion.
  • the formed rectangular recess has a spiral pitch of 0.9 mm per circumference on the surface of the steel material, each opening has a size of 80 ⁇ m ⁇ 320 ⁇ m, and an area ratio to the steel material surface area is 5%.
  • the depth of the formed recesses was an average of 1.5 ⁇ m, and the depth range (from the minimum value to the maximum value) was from 0.5 ⁇ m to 2.5 ⁇ m.
  • the surface was polished to remove burrs around the recess, and a shaft having a surface roughness (Ra) of 0.02 ⁇ m was obtained.
  • Example 2 A shaft was obtained in the same manner as in Example 1 except that the tool was changed and the average depth of the recesses was 2.5 ⁇ m and the depth range was 1.5 ⁇ m to 4 ⁇ m.
  • Example 3 A shaft was obtained in the same manner as in Example 1 except that the tool was changed and the average depth of the recesses was 3 ⁇ m and the depth range was 1.5 ⁇ m to 4.5 ⁇ m.
  • Example 4 A shaft was obtained in the same manner as in Example 1 except that the tool was changed and the average depth of the recesses was 10 ⁇ m and the depth range was 8 ⁇ m to 12 ⁇ m.
  • Example 5 A shaft was obtained in the same manner as in Example 1 except that the tool was changed and the average depth of the recesses was 13 ⁇ m and the depth range was 11 ⁇ m to 15 ⁇ m.
  • Example 2 A shaft was obtained in the same manner as in Example 1 except that the tool was changed and the average depth of the recesses was 0.5 ⁇ m and the depth range was 0.1 ⁇ m to 1 ⁇ m.
  • Example 3 A shaft was obtained in the same manner as in Example 1 except that the tool was changed and the average depth of the recesses was 17 ⁇ m and the depth range was 14 ⁇ m to 20 ⁇ m.
  • Example 4 A shaft was obtained in the same manner as in Example 1 except that the tool was changed and the average depth of the recesses was 20 ⁇ m and the depth range was 15 ⁇ m to 25 ⁇ m.
  • Example 5 A shaft was obtained in the same manner as in Example 1 except that the tool was changed and the average depth of the recesses was 3 ⁇ m and the depth range was 0.3 ⁇ m to 7 ⁇ m.
  • Example 6 A shaft was obtained in the same manner as in Example 1 except that the tool was changed and the average depth of the recesses was 13 ⁇ m and the depth range was 8 ⁇ m to 18 ⁇ m.
  • the shaft was combined with a bearing metal made of an Al—Sn alloy having a surface roughness of Ra 0.07 ⁇ m, and a seizure resistance test was performed using a bearing tester.
  • the shaft In the seizure test at low speed, in order to confirm the difference in lubricating oil retention, the shaft is rotated at a very low peripheral speed of 0.3 m / s, and the bearing metal is perpendicular to the connecting metal for the VQ35DE engine made by Nissan Motor.
  • the load was increased by increasing the projected surface pressure in 5 MPa steps until the point where the rotational torque value suddenly increased.
  • a lubricating oil a general-purpose engine oil having a viscosity of 5w-30 was used, and a maximum of about 10 cc / min was supplied.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Ocean & Marine Engineering (AREA)
  • Sliding-Contact Bearings (AREA)

Abstract

Selon la présente invention, de multiples parties évidées sont disposées dans une surface d'arbre, les profondeurs des parties évidées étant définies de façon se trouver dans une plage souhaitée, et la profondeur moyenne des parties évidée étant définie de façon à se trouver dans une plage souhaitée.
PCT/JP2015/080066 2014-11-07 2015-10-26 Palier lisse rotatif Ceased WO2016072305A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2014226877 2014-11-07
JP2014-226877 2014-11-07

Publications (1)

Publication Number Publication Date
WO2016072305A1 true WO2016072305A1 (fr) 2016-05-12

Family

ID=55909031

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/JP2015/080066 Ceased WO2016072305A1 (fr) 2014-11-07 2015-10-26 Palier lisse rotatif

Country Status (1)

Country Link
WO (1) WO2016072305A1 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US11739788B2 (en) 2018-08-31 2023-08-29 Nippon Steel Corporation Crankshaft and method of manufacturing the same
US12031577B2 (en) 2020-02-25 2024-07-09 Nippon Steel Corporation Crankshaft and method of manufacturing the same

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2006017218A (ja) * 2004-07-01 2006-01-19 Nissan Motor Co Ltd 摺動装置
JP2009192029A (ja) * 2008-02-18 2009-08-27 Nissan Motor Co Ltd 回転軸、これを用いた摺動装置、回転軸の加工装置、回転軸の加工方法、クランクシャフト、カムシャフト及びエンジン

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2006017218A (ja) * 2004-07-01 2006-01-19 Nissan Motor Co Ltd 摺動装置
JP2009192029A (ja) * 2008-02-18 2009-08-27 Nissan Motor Co Ltd 回転軸、これを用いた摺動装置、回転軸の加工装置、回転軸の加工方法、クランクシャフト、カムシャフト及びエンジン

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US11739788B2 (en) 2018-08-31 2023-08-29 Nippon Steel Corporation Crankshaft and method of manufacturing the same
US12031577B2 (en) 2020-02-25 2024-07-09 Nippon Steel Corporation Crankshaft and method of manufacturing the same

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