WO2016072305A1 - Rotational sliding bearing - Google Patents

Rotational sliding bearing 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
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WIPO (PCT)
Prior art keywords
shaft
bearing
sliding
recesses
concave portion
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PCT/JP2015/080066
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French (fr)
Japanese (ja)
Inventor
樋口　毅
大祐 鶴丸
和彦 高嶋
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日産自動車株式会社
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Publication of WO2016072305A1 publication Critical patent/WO2016072305A1/en

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    • 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.

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

Abstract

In the present invention, multiple recessed parts are disposed in a shaft surface, the depths of the recessed parts are set so as to be within a desired range, and the average depth of the recessed parts is set so as to be within a desired range.

Description

回転すべり軸受けRotating sliding bearing
　本発明は回転すべり軸受けに関し、更に詳細には摩擦低減と耐焼き付き性とを両立させた回転すべり軸受けに関する。 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.
　高速で摺動される内燃機関用摺動部材においては、摺動面間に潤滑油を供給し、摺動部材表面の表面粗さよりも大きい連続潤滑油膜を形成することで、摺動面の摩耗や焼付きを防止している。 In a sliding member for an internal combustion engine that is slid at high speed, 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.
　しかし、温度上昇に伴う潤滑油の粘度低下や潤滑油供給量の低下が起こると潤滑油膜が薄くなったり、油膜が切れたりして、摺動部材表面同士が接触し、摩耗や焼き付きが生じるため、摺動面間に潤滑油を供給するのみでは不十分である。特に表面粗さが小さく摩擦が低減された部材間において顕著である。 However, if the viscosity of the lubricating oil decreases or the supply amount of the lubricating oil decreases as the temperature rises, the lubricating oil film becomes thin or the oil film breaks, and the sliding member surfaces come into contact with each other, causing wear and seizure. It is not sufficient to supply lubricating oil between the sliding surfaces. This is particularly noticeable between members with small surface roughness and reduced friction.
　そこで、摺動面に微細凹部を多数形成し、摺動面上での保油性を向上させて、摺動面間に生じる摩擦を低減することが行われている。
　摺動部材においては、摺動面に多数の凹部を設けることで、前記凹部がオイルプールの役割を果たし、摺動させることで潤滑油層に圧力変動が生じ、ベアリングのような摺動特性が得られる。すなわち、摺動状態における潤滑油層の油圧の分布が、凹部の内側においては油圧が低くなり、凹部の縁において油圧が高くなって、部材間の間隔が拡げられる。
　この摺動する２つの部材間の油圧の分布状態は、オイルプールの形状や寸法などで決定され、オイルプールが多数存在することで、少量かつ低粘度の潤滑油でも高潤滑が可能となり耐焼付き性を向上させることができる。 Therefore, it has been practiced to reduce the friction generated between the sliding surfaces by forming a large number of fine recesses on the sliding surface to improve the oil retaining property on the sliding surface.
In the sliding member, by providing a large number of recesses on the sliding surface, 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.
　しかし、自動車用エンジンのクランクシャフト軸受け等、軸の直径方向に大きな荷重がかかる回転すべり軸受けは、もともと、上記荷重によって潤滑油膜が薄層化され易い。そして、温度上昇による潤滑油の粘度低下や、潤滑油の供給量低下が起こり、潤滑油膜切れが生じると軸と軸受けとが直接接触して、摩耗や焼き付きが生じ易い。 However, in the case of a rotational slide bearing that applies a large load in the diameter direction of the shaft, such as a crankshaft bearing of an automobile engine, the lubricating oil film tends to be thinned by the above load. When the viscosity of the lubricating oil decreases or the supply amount of the lubricating oil decreases due to a temperature rise and the lubricating oil film is cut, the shaft and the bearing are in direct contact with each other and wear and seizure are likely to occur.
　高粘度の潤滑油を使用すれば、潤滑油膜が厚くなり油膜が切れ難くなって、摩耗・焼き付きを防止できるが、潤滑油の内部摩擦が大きくなり、摩擦損失が大きくなってしまう。 If a high-viscosity lubricating oil is used, 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.
　したがって、回転すべり軸受けにおいて、摩擦低減と耐焼付き性とを両立させるためには、あらゆる条件下において、可能な限り油膜を薄くしつつ、油膜切れの発生を防止して軸と軸受けとが直接接触しないようにする必要があり、凹部形状の設定は困難を極める。 Therefore, in order to achieve both friction reduction and seizure resistance in rotating sliding bearings, 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.
　特許文献１の日本国特許第４２６９７２６号公報には、摺動面に硬質炭素皮膜を設けると共に、軸端部には浅い凹部を設け、軸中央部には深い凹部を設けた摺動部材が開示されている。 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.
　また、特許文献２の日本国特表２０１１－５０６８５５号公報には、軸の表面粗さが小さく、軸受けの「ならし」又は「なじみ」が行われない場合であっても、軸受けの表面粗さを所定の粗さ以下にすることで、摺動抵抗を低減できる旨が開示されている。 Further, 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.
　特許文献１及び特許文献２に記載のものは、すべり軸受けが安定的に回転し油膜圧力を発生させている状況においては摩擦力を低減できるものである。しかし、近年ではエンジンの高出力化に伴って軸が受ける荷重が大きくなってきており、運転条件等により、温度上昇による極端な粘度低下や潤滑油の供給量低下が起こった場合に、大きな荷重を受けることで油膜が切れやすい箇所があり、部品同士が直接接触してしまう。運転条件が厳しくなることで油膜切れの頻度が増え、焼付きにつながるリスクが高まっている状況である。 The ones described in 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. However, in recent years, 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. There is a part where the oil film is easily cut by receiving, and the parts are in direct contact with each other. As the operating conditions become severe, the frequency of oil film breakage increases and the risk of seizure increases.
　本発明は、このような従来技術の有する課題に鑑みてなされたものであり、その目的とするところは、油膜切れの頻度を抑えることで、どのような運転条件下においても安定して摩擦低減と耐焼き付き性とを両立できる回転すべり軸受けの提供を目的とする。 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.
　本発明者は、上記目的を達成すべく鋭意検討を重ねた結果、軸表面に設ける凹部の深さを所望の範囲内にすることにより、上記目的が達成できることを見出し、本発明を完成するに至った。 As a result of intensive studies to achieve the above object, 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.
　以下の詳細かつ具体的な説明から理解されるように、本発明によれば、軸表面に設ける凹部の深さを所望の範囲内にすることとしたため、大きな荷重を受けても、低速から高速のあらゆる運転条件下において、安定して摩擦低減と耐焼き付き性とを両立できるだけでなく、耐焼付き性を大幅に向上させた回転すべり軸受けを提供することができる。 As will be understood from the following detailed and specific description, according to the present invention, the depth of the concave portion provided on the shaft surface is set within a desired range. Thus, it is possible to provide a rotary sliding bearing that can not only stably achieve both friction reduction and seizure resistance, but also greatly improve seizure resistance.
本発明の回転滑り軸受けの一例を示す図である。It is a figure which shows an example of the rotation sliding bearing of this invention. 軸表面の凹部と油膜の圧力分布の関係を示す模式図である。It is a schematic diagram which shows the relationship between the recessed part of a shaft surface, and the pressure distribution of an oil film.
　本発明の回転すべり軸受けについて詳細に説明する。
　本発明の回転軸受けの一例を図１に示す。図１は、軸方向に対して垂直方向に切ったところの一例を示す断面図であり、図１（ｂ）は、軸の摺動面の一例を示す模式図である。
　本発明の回転すべり軸受け１は、軸２と軸受け３とが潤滑油４の存在下で摺接するものであり、軸２の摺動面には、多数の凹部２１が規則的に形成される。
　ここで、規則的とはある単位面積における凹部の分布状態と他の単位面積における凹部の分布状態とが同じであれば足り、凹部が等間隔に形成されていなくてもよい。 The rotary slide bearing of the present invention will be described in detail.
An example of the rotary bearing of the present invention is shown in FIG. FIG. 1 is a cross-sectional view illustrating an example of a section cut in a direction perpendicular to the axial direction, and FIG. 1B is a schematic diagram illustrating an example of a sliding surface of the shaft.
In the rotary sliding bearing 1 of the present invention, 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.
Here, it is sufficient that 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.
　上記軸表面に形成された多数の凹部２１は、深さの範囲が０．５μｍ～１５μｍであり、さらに１．５～１５μｍであることが好ましい。摺動面の潤滑油膜の圧力分布は、図２に示すように、凹部の内側で油圧が低くなり、凹部の縁で油圧が高くなる。
　深さが０．５μｍ未満の凹部があると、保油量が十分でなく、また圧力差も生じにくいため、油膜厚さを増大させる効果はほとんど望めない。また、凹部の深さが深いほど保油量は多くなるが、１５μｍを超える凹部が存在すると、高面圧・高速運転時において局所的な圧力変動が大きくなって、凹部の内部において油圧が極端に低くなり、微視的には油膜を形成し難くなる箇所が生じて、耐焼付き性が低下する。 The number of recesses 21 formed on the shaft surface has a depth range of 0.5 μm to 15 μm, and more preferably 1.5 to 15 μm. As shown in FIG. 2, 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 μm, 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. In addition, the oil retention increases as the depth of the recess increases, but if there is a recess exceeding 15 μm, 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.
　また、多数の凹部２１の深さの平均は、１．５μｍ以上１５μｍ以下であり、３μｍ以上１５μｍ以下であることが好ましい。深さの平均が１．５μｍ未満であると保油量が少なく油膜切れの頻度が増加する。 Moreover, the average depth of the many recesses 21 is 1.5 μm or more and 15 μm or less, and preferably 3 μm or more and 15 μm or less. When the average depth is less than 1.5 μm, the amount of oil retention is small and the frequency of oil film breakage increases.
　前記凹部の深さの測定は、例えば、三次元表面構造解析顕微鏡を用い、非接触三次元白色光位相変調干渉方式などにより測定することができる。 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.
　すべり軸受けにおいては、大きな荷重を受けた際に軸が弾性変形することで、例えば、低速運転時に摺動面の潤滑油が枯渇した際にも凹部から潤滑油の２次的供給が行われ、焼き付きが防止される。 In the sliding bearing, 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.
　本発明の軸は、表面硬さ（ロックウェル硬度）が４５ＨＲｃ以上６５ＨＲｃ以下であることが好ましい。４５ＨＲｃ以上とすることで耐摩耗性が向上し、また６５ＨＲｃ以下とすることで靱性を確保して耐衝撃性を向上させることができる。
　なお、硬度ＨＲｃはＪＩＳＺ２２４５に規定されるロックウェル硬度のＣスケールを示す。 The shaft of the present invention preferably has a surface hardness (Rockwell hardness) of 45HRc or more and 65HRc or less. By setting it to 45 HRc or more, wear resistance can be improved, and by setting it to 65 HRc or less, toughness can be ensured and impact resistance can be improved.
The hardness HRc indicates the C scale of Rockwell hardness defined in JISZ2245.
　また、本発明の軸は、凹部以外の箇所の表面粗さ（Ｒａ）が０．１０μｍ以下であることが好ましい。上記凹部以外の箇所は、軸受けと接触し易い箇所であり、表面粗さ（Ｒａ）をこの範囲とすることで油膜厚さが薄くなった場合にも軸受けとの接触を抑えることができ、摩擦損失低減効果をもたらすものである。 Further, in the shaft of the present invention, it is preferable that the surface roughness (Ra) of portions other than the recesses is 0.10 μm 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.
　軸表面の凹部の開口部形状は、矩形又は楕円形であり、該矩形の長辺方向又は楕円形の長径方向と、すべり方向とが直交することが好ましい。長辺方向又は長径方向がすべり方向と直交することで、油圧が高い箇所を広範囲に形成でき、ベアリングのような摺動特性が得られて耐焼付き性が向上する。 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.
　軸表面に対する開口部の面積率は、１％以上１０％以下であることが好ましい。この範囲とすることで十分な油保持性を確保し、平坦部面積を確保して耐焼付きに対する負荷容量を維持し、凹部形成による効果を発現できる。上記面積率は、例えば、表面観察写真を画像処理することにより算出できる。 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.
　なお、矩形又は楕円形の短辺・短径方向の長さは短いほど好ましい。具体的には使用する潤滑油の粘度にもよるが、５０μｍ以上１５０μｍ以下であることが好ましく、５０μｍ以上１２０μｍ以下であることがより好ましい。この範囲にすることで加工コストを増加させることなく軸表面の凹部密度を維持できることとなる。
　また、長辺・長径方向の長さは２００μｍ以上５００μｍ以下であることが好ましい。この範囲にすることで、凹部と凹部の間隔が適切な範囲となり、油膜圧力を維持することができて油膜厚さを増大する効果を維持できる。 In addition, it is preferable that 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 μm or more and 150 μm or less, and more preferably 50 μm or more and 120 μm 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 μm or more and 500 μm or less. By setting it as this range, the space | interval of a recessed part and a recessed part becomes an appropriate range, the oil film pressure can be maintained and the effect which increases an oil film thickness can be maintained.
　本発明の凹部は、凸形状の工具を軸表面に押し当て、形状を転写することによって形成できる（例えば、日本国特開２００４－２３７４０６号公報、日本国特開２００２－３６１３５１号公報）。凹部の形状や数量は工具の形状により一義的に決定し、深さは押込み荷重または工具の高さによって決まる。凹部の形成は必ずしもこの方法にはよらず、例えばレーザー光を照射する方法や、適当なマスクを準備した上で硬質粒子を投射する方法（日本国特開２００３－１３７１０号公報）によって形成してもよい。 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. For example, 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.
　凹部の加工により、凹部周辺に突起が形成される場合があるが、突起の高さは表面粗さの凹凸を超えない高さ（概ね０．１μｍ以下）に抑えることが好ましい。 Although protrusions may be formed around the recesses due to the processing of the recesses, the height of the protrusions is preferably suppressed to a height that does not exceed the unevenness of the surface roughness (approximately 0.1 μm or less).
　上記軸受は、シリンダー内の爆発力や運動部の慣性力からなる大きな荷重を支える軸受強度を備えると共に、高速で回転するクランクシャフトの運動に対して、それを阻害するような外乱要因からクランクシャフトもしくはエンジンを守るものである。
　このような軸受けは、荷重を支える軸受合金の表面に、なじみ性などの順応性を捕捉する厚さ数ミクロンのオーバレイが形成される場合がある。 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.
In such a bearing, 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.
　前記オーバレイとしては、アルミ、銅、鉛、錫、ビスマス、銀等の軟らかい金属や、ポリアミドイミド等のエンジニアリングプラスチックを単独又は混合して使用することができ、これらの材料にＰＴＦＥ、グラファイト、モリブテン等の多様な材料を添加することもできる。 As the overlay, soft metals such as aluminum, copper, lead, tin, bismuth, and silver, and engineering plastics such as polyamideimide can be used alone or in combination. These materials include PTFE, graphite, molybdenum, etc. It is also possible to add various materials.
　軸受けの表面粗さ（Ｒａ）は、０．１５μｍ以下であることが好ましい。この範囲とすることで耐焼付き性を向上できる。
　なお、上記軸表面の凹部に替えて、軸受け表面に凹部を設けてもよいが、軸受けの表面は、上記のように、なじみ性等の順応性有する軟らかい材料で形成されるため、微細な凹部を高精度で形成する場合にはその加工に時間を要することがある。 The surface roughness (Ra) of the bearing is preferably 0.15 μm or less. By setting it within this range, seizure resistance can be improved.
In place of the concave portion on the shaft surface, a concave portion may be provided on the bearing surface. However, as described above, 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.
　本発明の回転すべり軸受けは、自動車用エンジンのクランクシャフト軸受けに好適に用いられる。 The rotary sliding bearing of the present invention is suitably used for a crankshaft bearing of an automobile engine.
　以下、本発明を実施例により詳細に説明するが、本発明は下記実施例に限定されるものではない。 Hereinafter, the present invention will be described in detail by way of examples, but the present invention is not limited to the following examples.
［実施例１］
　円柱形状のＳＶ４０Ｃ鋼材（ＪＩＳ　Ｇ４０５１に規定されたＳ４０Ｃ鋼に微量のバナジウム（Ｖ）を添加したもの）の表面に焼入れを行い表面硬さを５８ＨＲｃとした。
　凸部が円周に沿って1列に形成された円筒状工具を準備し、該工具の凸形状を上記鋼材の表面に転写、矩形凹部を形成した。形成された矩形凹部は、上記鋼材表面にらせん状に１周あたり０．９ｍｍピッチ、各開口部が８０μｍ×３２０μｍ、鋼材表面積に対する面積率が５％である。 [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 μm × 320 μm, and an area ratio to the steel material surface area is 5%.
　形成した凹部の深さは平均１．５μｍであり、深さの範囲（最小値から最大値まで）が０．５μｍから２．５μｍであった。該凹部を形成したのち、表面の研磨を行って凹部周辺のバリを除去し、表面粗さ（Ｒａ）が０．０２μｍのシャフトを得た。 The depth of the formed recesses was an average of 1.5 μm, and the depth range (from the minimum value to the maximum value) was from 0.5 μm to 2.5 μm. After forming the recess, the surface was polished to remove burrs around the recess, and a shaft having a surface roughness (Ra) of 0.02 μm was obtained.
［実施例２］
　工具を替え、凹部の平均深さを２．５μｍ、深さの範囲を１．５μｍ～４μｍとすること以外は実施例１と同様にしてシャフトを得た。 [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 μm and the depth range was 1.5 μm to 4 μm.
［実施例３］
　工具を替え、凹部の平均深さを３μｍ、深さの範囲を１．５μｍ～４・５μｍとすること以外は実施例１と同様にしてシャフトを得た。 [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 μm and the depth range was 1.5 μm to 4.5 μm.
［実施例４］
　工具を替え、凹部の平均深さを１０μｍ、深さの範囲を８μｍ～１２μｍとすること以外は実施例１と同様にしてシャフトを得た。 [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 μm and the depth range was 8 μm to 12 μm.
［実施例５］
　工具を替え、凹部の平均深さを１３μｍ、深さの範囲を１１μｍ～１５μｍとすること以外は実施例１と同様にしてシャフトを得た。 [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 μm and the depth range was 11 μm to 15 μm.
［比較例１］
　凹部を形成せずに表面を研磨して表面粗さ（Ｒａ）が０．０２μｍのシャフトを得た。 [Comparative Example 1]
The surface was polished without forming a recess to obtain a shaft having a surface roughness (Ra) of 0.02 μm.
［比較例２］
　工具を替え、凹部の平均深さを０・５μｍ、深さの範囲を０・１μｍ～１μｍとすること以外は実施例１と同様にしてシャフトを得た。 [Comparative 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 μm and the depth range was 0.1 μm to 1 μm.
［比較例３］
　工具を替え、凹部の平均深さを１７μｍ、深さの範囲を１４μｍ～２０μｍとすること以外は実施例１と同様にしてシャフトを得た。 [Comparative 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 μm and the depth range was 14 μm to 20 μm.
［比較例４］
　工具を替え、凹部の平均深さを２０μｍ、深さの範囲を１５μｍ～２５μｍとすること以外は実施例１と同様にしてシャフトを得た。 [Comparative 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 μm and the depth range was 15 μm to 25 μm.
［比較例５］
　工具を替え、凹部の平均深さを３μｍ、深さの範囲を０．３μｍ～７μｍとすること以外は実施例１と同様にしてシャフトを得た。 [Comparative 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 μm and the depth range was 0.3 μm to 7 μm.
［比較例６］
　工具を替え、凹部の平均深さを１３μｍ、深さの範囲を８μｍ～１８μｍとすること以外は実施例１と同様にしてシャフトを得た。 [Comparative 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 μm and the depth range was 8 μm to 18 μm.
［評価］
　上記の軸に、表面粗さがＲａ０．０７μｍのＡｌ－Ｓｎ系合金製軸受メタルを組合せ、軸受け試験機を使用して耐焼き付き性試験を実施した。 [Evaluation]
The shaft was combined with a bearing metal made of an Al—Sn alloy having a surface roughness of Ra 0.07 μm, and a seizure resistance test was performed using a bearing tester.
　低速時焼き付き試験は、潤滑油保持性の差を確認するため、ごく低速の０．３ｍ／ｓの周速で軸を回転させ、軸受けメタルに日産自動車製ＶＱ３５ＤＥエンジン用のコネクティングロッドを介して垂直荷重を加え、回転トルク値が急激に上昇するポイントまで、投影面圧を５ＭＰａステップで負荷を強めた。潤滑油は５ｗ－３０粘度の汎用エンジン油を用い、最大１０ｃｃ／ｍｉｎ程度を供給した。 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. As 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.
　次に、潤滑油の供給が十分であるが摩擦で温度が上昇した場合の耐焼付き性の確認として、高速時の焼き付き試験を行った。
　高速時の焼き付き試験は、１５ｍ／ｓの周速で軸を回転させ、常時７０ｃｃ／ｍｉｎの潤滑油を供給し続けた。荷重は、同様に投影面圧を５ＭＰａステップで負荷を強めていき、回転トルク値が８Ｎｍまたは油温度が２８０℃を越えたポイントを焼付き面圧とした。
　評価結果を表１にしめす。 Next, a seizure test at high speed was performed as a confirmation of seizure resistance when the lubricating oil was sufficiently supplied but the temperature increased due to friction.
In the seizure test at high speed, the shaft was rotated at a peripheral speed of 15 m / s, and the lubricant oil of 70 cc / min was continuously supplied. As for the load, the projected surface pressure was similarly increased in 5 MPa steps, and the point at which the rotational torque value was 8 Nm or the oil temperature exceeded 280 ° C. was defined as the seizing surface pressure.
The evaluation results are shown in Table 1.
Figure JPOXMLDOC01-appb-T000001
Figure JPOXMLDOC01-appb-T000001
　　１　　回転すべり軸受け
　　２　　軸
　　３　　軸受け
　　４　　潤滑油
　　２１　凹部　 1 Rotating sliding bearing 2 Shaft 3 Bearing 4 Lubricating oil 21 Recess
日本国特許第４２６９７２６号公報Japanese Patent No. 4269726 日本国特表２０１１－５０６８５５号公報Japanese National Table 2011-506855

Claims (8)

  1. 　軸受と、該軸受と潤滑油を介して摺接する軸とを有する回転すべり軸受けであって、
    　上記軸が表面に多数の凹部を有するものであり、
    　該多数の凹部の深さが０．５μｍ～１５μｍの範囲であり、深さの平均が１．５μｍ～１５μｍであることを特徴とする回転すべり軸受け。     A rotary sliding bearing having a bearing and a shaft that is in sliding contact with the bearing via lubricating oil,
    The shaft has a number of recesses on the surface,
    A rotary slide bearing characterized in that the depth of the plurality of recesses is in the range of 0.5 μm to 15 μm, and the average depth is 1.5 μm to 15 μm.
  2. 　上記軸の表面硬さ（ロックウェル硬度）が、４５ＨＲｃ～６５ＨＲｃであることを特徴とする請求項１に記載の回転すべり軸受け。 The rotary sliding bearing according to claim 1, wherein the shaft has a surface hardness (Rockwell hardness) of 45HRc to 65HRc.
  3. 　上記軸の凹部の深さの平均が３．０μｍ～１５μｍであることを特徴とする請求項１又は２に記載の回転すべり軸受け。 3. The rotary sliding bearing according to claim 1, wherein the average depth of the concave portion of the shaft is 3.0 μm to 15 μm.
  4. 　上記軸の凹部以外の箇所の表面粗さ（Ｒａ）が、０．１０μｍ以下であることを特徴とする請求項１～３のいずれか１つの項に記載の回転すべり軸受け。 The rotary sliding bearing according to any one of claims 1 to 3, wherein a surface roughness (Ra) of a portion other than the concave portion of the shaft is 0.10 µm or less.
  5. 　上記軸の凹部の開口部形状が矩形又は楕円形であり、開口部の長辺方向又は長径方向と、すべり方向とが、直交することを特徴とする請求項１～４のいずれか１つの項に記載の回転すべり軸受け。 The opening according to any one of claims 1 to 4, wherein the shape of the opening of the concave portion of the shaft is a rectangle or an ellipse, and the long side direction or the long diameter direction of the opening is perpendicular to the sliding direction. Rotating slide bearing as described in
  6. 　上記軸表面の凹部の開口部の軸表面に対する面積率が、１～１０％であることを特徴とする請求項１～５のいずれか１つの項に記載の回転すべり軸受け。 The rotary sliding bearing according to any one of claims 1 to 5, wherein an area ratio of the opening of the concave portion on the shaft surface to the shaft surface is 1 to 10%.
  7. 　上記軸受の表面粗さ（Ｒａ）が、０．１５μｍ以下であることを特徴とする請求項１～６のいずれか１つの項に記載の回転すべり軸受け。 The rotary sliding bearing according to any one of claims 1 to 6, wherein the bearing has a surface roughness (Ra) of 0.15 µm or less.
  8. 　自動車用エンジンのクランクシャフト軸受けに用いられることを特徴とする請求項１～７のいずれか１つの項に記載の回転すべり軸受け。 The rotary slide bearing according to any one of claims 1 to 7, which is used for a crankshaft bearing of an automobile engine.
PCT/JP2015/080066 2014-11-07 2015-10-26 Rotational sliding bearing WO2016072305A1 (en)

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Cited By (1)

* 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

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2006017218A (en) * 2004-07-01 2006-01-19 Nissan Motor Co Ltd Sliding device
JP2009192029A (en) * 2008-02-18 2009-08-27 Nissan Motor Co Ltd Rotating shaft, sliding device using same, machining device of rotating shaft, machining method of rotating shaft, crank shaft, cam shaft, and engine

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2006017218A (en) * 2004-07-01 2006-01-19 Nissan Motor Co Ltd Sliding device
JP2009192029A (en) * 2008-02-18 2009-08-27 Nissan Motor Co Ltd Rotating shaft, sliding device using same, machining device of rotating shaft, machining method of rotating shaft, crank shaft, cam shaft, and engine

Cited By (1)

* 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

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