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TW200848503A - Grease for high-speed bearing and rolling bearing for high speed - Google Patents

Grease for high-speed bearing and rolling bearing for high speed Download PDF

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Publication number
TW200848503A
TW200848503A TW097106632A TW97106632A TW200848503A TW 200848503 A TW200848503 A TW 200848503A TW 097106632 A TW097106632 A TW 097106632A TW 97106632 A TW97106632 A TW 97106632A TW 200848503 A TW200848503 A TW 200848503A
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TW
Taiwan
Prior art keywords
oil
bearing
speed
lubricating oil
rolling bearing
Prior art date
Application number
TW097106632A
Other languages
Chinese (zh)
Other versions
TWI454568B (en
Inventor
Takayuki Kawamura
Hidenobu Mikami
Kenji Tamada
Original Assignee
Ntn Toyo Bearing Co Ltd
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Filing date
Publication date
Priority claimed from JP2007046258A external-priority patent/JP5305600B2/en
Priority claimed from JP2007134670A external-priority patent/JP2008286372A/en
Priority claimed from JP2007171804A external-priority patent/JP2009008209A/en
Priority claimed from JP2007198443A external-priority patent/JP2009036221A/en
Priority claimed from JP2007293879A external-priority patent/JP2009121531A/en
Application filed by Ntn Toyo Bearing Co Ltd filed Critical Ntn Toyo Bearing Co Ltd
Publication of TW200848503A publication Critical patent/TW200848503A/en
Application granted granted Critical
Publication of TWI454568B publication Critical patent/TWI454568B/en

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    • C—CHEMISTRY; METALLURGY
    • C10—PETROLEUM, GAS OR COKE INDUSTRIES; TECHNICAL GASES CONTAINING CARBON MONOXIDE; FUELS; LUBRICANTS; PEAT
    • C10M—LUBRICATING COMPOSITIONS; USE OF CHEMICAL SUBSTANCES EITHER ALONE OR AS LUBRICATING INGREDIENTS IN A LUBRICATING COMPOSITION
    • C10M169/00—Lubricating compositions characterised by containing as components a mixture of at least two types of ingredient selected from base-materials, thickeners or additives, covered by the preceding groups, each of these compounds being essential
    • C10M169/02—Mixtures of base-materials and thickeners
    • 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
    • F16C33/30—Parts of ball or roller bearings
    • F16C33/66—Special parts or details in view of lubrication
    • F16C33/6603—Special parts or details in view of lubrication with grease as lubricant
    • F16C33/6633—Grease properties or compositions, e.g. rheological properties
    • C—CHEMISTRY; METALLURGY
    • C10—PETROLEUM, GAS OR COKE INDUSTRIES; TECHNICAL GASES CONTAINING CARBON MONOXIDE; FUELS; LUBRICANTS; PEAT
    • C10M—LUBRICATING COMPOSITIONS; USE OF CHEMICAL SUBSTANCES EITHER ALONE OR AS LUBRICATING INGREDIENTS IN A LUBRICATING COMPOSITION
    • C10M2207/00—Organic non-macromolecular hydrocarbon compounds containing hydrogen, carbon and oxygen as ingredients in lubricant compositions
    • C10M2207/04—Ethers; Acetals; Ortho-esters; Ortho-carbonates
    • C10M2207/0406—Ethers; Acetals; Ortho-esters; Ortho-carbonates used as base material
    • C—CHEMISTRY; METALLURGY
    • C10—PETROLEUM, GAS OR COKE INDUSTRIES; TECHNICAL GASES CONTAINING CARBON MONOXIDE; FUELS; LUBRICANTS; PEAT
    • C10M—LUBRICATING COMPOSITIONS; USE OF CHEMICAL SUBSTANCES EITHER ALONE OR AS LUBRICATING INGREDIENTS IN A LUBRICATING COMPOSITION
    • C10M2207/00—Organic non-macromolecular hydrocarbon compounds containing hydrogen, carbon and oxygen as ingredients in lubricant compositions
    • C10M2207/28—Esters
    • C10M2207/2805—Esters used as base material
    • C—CHEMISTRY; METALLURGY
    • C10—PETROLEUM, GAS OR COKE INDUSTRIES; TECHNICAL GASES CONTAINING CARBON MONOXIDE; FUELS; LUBRICANTS; PEAT
    • C10M—LUBRICATING COMPOSITIONS; USE OF CHEMICAL SUBSTANCES EITHER ALONE OR AS LUBRICATING INGREDIENTS IN A LUBRICATING COMPOSITION
    • C10M2215/00—Organic non-macromolecular compounds containing nitrogen as ingredients in lubricant compositions
    • C10M2215/10—Amides of carbonic or haloformic acids
    • C10M2215/102—Ureas; Semicarbazides; Allophanates
    • C10M2215/1026—Ureas; Semicarbazides; Allophanates used as thickening material
    • C—CHEMISTRY; METALLURGY
    • C10—PETROLEUM, GAS OR COKE INDUSTRIES; TECHNICAL GASES CONTAINING CARBON MONOXIDE; FUELS; LUBRICANTS; PEAT
    • C10N—INDEXING SCHEME ASSOCIATED WITH SUBCLASS C10M RELATING TO LUBRICATING COMPOSITIONS
    • C10N2020/00—Specified physical or chemical properties or characteristics, i.e. function, of component of lubricating compositions
    • C10N2020/01—Physico-chemical properties
    • C10N2020/02—Viscosity; Viscosity index
    • C—CHEMISTRY; METALLURGY
    • C10—PETROLEUM, GAS OR COKE INDUSTRIES; TECHNICAL GASES CONTAINING CARBON MONOXIDE; FUELS; LUBRICANTS; PEAT
    • C10N—INDEXING SCHEME ASSOCIATED WITH SUBCLASS C10M RELATING TO LUBRICATING COMPOSITIONS
    • C10N2030/00—Specified physical or chemical properties which is improved by the additive characterising the lubricating composition, e.g. multifunctional additives
    • C10N2030/06—Oiliness; Film-strength; Anti-wear; Resistance to extreme pressure
    • C—CHEMISTRY; METALLURGY
    • C10—PETROLEUM, GAS OR COKE INDUSTRIES; TECHNICAL GASES CONTAINING CARBON MONOXIDE; FUELS; LUBRICANTS; PEAT
    • C10N—INDEXING SCHEME ASSOCIATED WITH SUBCLASS C10M RELATING TO LUBRICATING COMPOSITIONS
    • C10N2040/00—Specified use or application for which the lubricating composition is intended
    • C10N2040/02—Bearings
    • C—CHEMISTRY; METALLURGY
    • C10—PETROLEUM, GAS OR COKE INDUSTRIES; TECHNICAL GASES CONTAINING CARBON MONOXIDE; FUELS; LUBRICANTS; PEAT
    • C10N—INDEXING SCHEME ASSOCIATED WITH SUBCLASS C10M RELATING TO LUBRICATING COMPOSITIONS
    • C10N2050/00—Form in which the lubricant is applied to the material being lubricated
    • C10N2050/10—Semi-solids; greasy
    • 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
    • F16C19/00—Bearings with rolling contact, for exclusively rotary movement
    • F16C19/02—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows
    • F16C19/04—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for radial load mainly
    • F16C19/06—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for radial load mainly with a single row or balls
    • 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
    • F16C19/00—Bearings with rolling contact, for exclusively rotary movement
    • F16C19/02—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows
    • F16C19/14—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load
    • F16C19/16—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with a single row of balls
    • F16C19/163—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with a single row of balls with angular contact
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C2202/00—Solid materials defined by their properties
    • F16C2202/66—Water repelling

Landscapes

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

Abstract

A grease for high-speed bearing and rolling bearing for high speed that enable satisfactorily coping with a high-speed rotation of 170OE0<4> or higher dmN value and enable realizing compaction of machine tool and cutback of operating costs. The grease is one comprising a base oil and a urea thickener, wherein the base oil has a kinematic viscosity of 15 to 30 mm<2>/sec at 40 DEG C, and wherein the urea thickener is one obtained by reaction between a polyisocyanate component and a monoamine component, the monoamine component containing 50 mol% or more of at least one monoamine selected from among aliphatic monoamines and alicyclic monoamines based on all the monoamines, and is contained in an amount of 3 to less than 9 wt.% based on the total amount of the grease.; Rolling bearing for high speed (1) is one comprising inner ring (2), outer ring (3), multiple rolling elements (4) interposed between the inner ring (2) and the outer ring (3) and seal member (6), wherein the above grease (8) is hermetically introduced around the rolling elements(4).

Description

200848503 九、發明說明 【發明所屬之技術領域】 本發明係關於用來支承工作機械主軸（s p j n d丨e ) 局速轉軸的滾動軸承所使用之高速軸承用潤滑油、以 該潤滑油封入內部之高速用滾動軸承 【先前技術】 工作機械的主軸，爲提昇加工效率須進行高速旋 其軸承是運用各種的潤滑技術。適用於高速旋轉的主 潤滑方法，例如包括油霧潤滑、油氣潤滑、噴射潤滑 方法。 然而’這些潤滑方法，由於須設置壓縮空氣和供 置等的附帶設備，會造成工作機械的購置成本和運轉 昇高’相對於此，潤滑油潤滑由於維修保養的必要性 可說是較佳的潤滑方法。例如，就用來支承以2 0 0 0〜 rpm或更高速來旋轉的轉軸之高速用滾動軸承而言， 括：用來支承工作機械主軸（spindle )之斜角滾珠軸 圓柱滾子軸承等等。 第1 4圖所示之斜角滾珠軸承5 1，除負荷徑荷重 能負荷一方向的軸荷重，由鋼球5 4和內環5 2及外 的接觸點連接成的直線，相對於徑方向具有夾角（ 角）α。在內環5 2和外環5 3和鋼球5 4所形成的軺 間內封入潤滑油。 作爲由斜角丨孩珠軸承、圓柱滾子軸承等構成的 等的 及將 轉， 軸之 等的 油裝 費用 低， 8000 是包 承、 ，也 1 53 接觸 承空 速用 -5 - 200848503 滾動軸承所使用的潤滑劑，較佳爲採用不須進行供油等的 維修保養且將稠度調整成不致污染周圍環境之潤滑油。 關於主軸用滾動軸承等的高速用滾動軸承使用的潤滑 油所要求之潤滑特性和問題點，可整理如下。 (a )爲了儘量延長長壽命滾動軸承的潤滑壽命，如 以下（i )〜（iii )所說明，必須符合：潤滑劑（潤滑油 或其基油）不容易從滾動軸承漏出、潤滑油的耐熱性優 異、可形成潤滑所需的油膜厚度等的要求。 (i )在滾動軸承高速運轉時，離心力會使滾動軸承 內的潤滑油流向軸承外部，或使潤滑油中的基油分離流 出，而不容易留在須筒度潤滑的滾道面附近，因此容易發 生潤滑不良。爲了防止這種事態發生，其對策是將密封板 等的板構件裝設在滾動軸承。然而，依軸承的構造，可能 發生無法裝設的情形，又即使裝設密封構件，仍可能發生 無法將潤滑劑或潤滑油完全密封的情形。 在非高速運轉的滾動軸承的情形，因轉動體或保持器 的運動而從摩擦部分擠出的多餘的潤滑油，依旋轉條件會 以一定程度回流至軸承內部而再度進行潤滑。但是，在高 速旋轉的工作機械等的轉軸支承用滾動軸承，由於軸承內 部發生的風壓會阻礙回流的進行，故潤滑油難以供應至滾 道部’而容易發生潤滑不良。因此，在高速旋轉的滾動軸 承，僅少量的潤滑油是用於潤滑，故潤滑油的性質特別重 要。高速用滾動軸承所使用的潤滑油，必須要求既使在少 量的潤滑油下仍能維持潤滑性能。 -6 - 200848503 (i i)在運轉條件高速化時，軸承的滾動面 熱而形成高溫，這時耐熱性差的潤滑油會發生熱 造成潤滑油的壽命顯著縮短。針對此問題，已嘗 有耐熱性的增稠劑或基油，或是添加氧化防止劑 嘗試，都無法到達令人滿意的耐久性提昇。 (ni)提昇潤滑性（油膜厚度）之習知的潤 基油黏度變高，剪切摩擦阻力變大而造成轉矩增 量增大，爲了抑制這些現象是將基油黏度減低。 高速運轉所伴生的溫度上昇而變成低黏度的潤滑 變薄，如此可能會發生滑動摩耗。 (b )具有低轉矩性（溫度上昇抑制性）之 速軸承用潤滑油，雖如前述般可將基油黏度減低 承高速旋轉時，溫度上昇會造成黏度明顯降低， 成潤滑所須厚度的油膜。 (c )關於低振動性的潤滑油，依增稠劑的 會造成軸承的振動變大。亦即，所含的增稠劑會 硬的凝集體之潤滑油的情形，受潤滑之滾動軸承 變大。 這種習知的潤滑油，在運用於高速用滾動 形’並無法符合軸承的長壽命性、低轉矩性、但 物性的要求。作爲其對策，雖有配合脲化合物的 提出（參照專利文獻1〜專利文獻3 )，但油 大’要獲得更高速的性能尙嫌不足。 例如，專利文獻3揭示的潤滑油組成物，俏 會局部發 劣化，而 試使用具 ，但這些 滑油，若 大且發熱 因此，因 油油膜會 既有的高 ，但當軸 而無法形 種類可能 形成大且 的振動會 軸承的情 振動性等 潤滑油被 消耗量變 含有：40 -7- 200848503 °C的動黏度爲1 5 mm2/sec以上40 mm2/sec以下的基油、 含量佔潤滑油組成物全體的9質量％以上1 4質量％以下之 二脲化合物的增稠劑，且混合稠度爲2 2 0以上3 2 0以下。 然而，在上述潤滑油組成物也是，要減少增稠劑的配 合量以減低潤滑油封入量會有困難，又無法充分對應於軸 承的高速旋轉，要謀求工作機械的緊致化和運轉費用的降 低會有困難。 再者，近年來滾動軸承的使用狀態越來越嚴苛，在節 圓直徑dm ( mm )和轉數N ( rpm )的乘積（dmN値）爲 1 7 〇萬以上的高速旋轉所使用的主軸用滾動軸承等也變多 起來。隨著如此般軸承的旋轉速度的高速化，既有的潤滑 油要完全符合軸承所要求的性能相當困難。 專利文獻1:日本特開2000-169872號公報 專利文獻2:日本特開2003-83341號公報 專利文獻3:日本特開2006-29473號公報 【發明內容】 本發明係有鑑於這種狀況而構成者，其目的是爲了提 供一種可使用於滾動軸承的高速軸承用潤滑油，即使以較 少的潤滑油封入量，仍能對應於例如節圓直徑dm ( mm ) 和轉數N ( rpm )的乘積（dmN値）爲丨7〇萬以上的高速 旋轉’而能謀求工作機械等的緊致化和運轉經費的降低； 又提供一種將該潤滑油封入內部之高速用滾動軸承。 本發明之局速軸承用潤滑油，其特徵在於··係含有基 -8- 200848503 油和脲系增稠劑，上述基油在 4 0 °C的動黏度爲 15 mm2/sec〜30 mm2/sec，上述脲系增稠劑是將聚異氰酸酯成 分和單胺成分反應而製得；該單胺成分，是相對於單胺全 體含有5 0莫耳％以上的選自脂肪族單胺及脂環式單胺中至 少1種單胺之單胺成分；相對於潤滑油全體，上述脲系增 稠劑含量爲3重量％以上9重量％未滿。 此外，上述基油的表面張力爲25 mN/m以上，且密度 爲 0.95 g/cm3 以下。 又上述基油，係選自合成烴油、酯油、烷基二苯醚油 中至少1種油。 本發明的高速用滾動軸承，係用來支承以高速旋轉的 軸之高速用滾動軸承，其特徵在於：該滾動軸承係具備： 內環及外環、介設於內環及外環間之複數個轉動體、用來 保持該轉動體的保持器、將上述內環及外環間的間隙的開 口予以覆蓋之密封構件；在上述轉動體的周圍封入潤滑 油，該潤滑油是使用上述本發明的高速軸承用潤滑油。 此外，在選自上述內環的滾道面表面、上述外環的滾 道面表面、上述轉動體的表面中至少一個，實施凹坑加 工。 又上述凹坑加工爲珠擊加工，藉由該加工而形成於各 表面的凹坑，從該表面起算的深度爲〇 · 1〜1 〇 # m ° 又在選自上述內環的外徑面、上述外環的內徑面以及 上述轉動體的表面中至少一個，形成被膜。 又上述被膜，係藉由金屬鍍敷處理或磷酸被膜處理所 -9· 200848503 形成的被膜。 又上述保持器，係在袋孔部（pocket )的內面具有凹 部’且至少該凹部的緣部被去角。 又上述凹部，係儲油部或離隙部。 又上述保持器是樹脂製的保持器。 又上述保持器所使用的樹脂，係聚醯胺（以下稱 PA)樹脂、酚樹脂或聚醚醚酮（以下稱PEEK)樹脂。 又在與上述潤滑油接觸之軸承內部表面的至少一部 分，形成撥水撥油性被膜。 又，上述撥水撥油性被膜係形成於：選自（1 )密封 構件的軸承內部側表面的一部分、（2 )外環之除軌道面 以外的內徑面及密封構件的軸承內部側表面、（3 )內環 之除軌道面以外的外徑面及密封構件的軸承內部側表面、 (4)除與轉動體的接觸面以外之保持器的表面中至少一. 個。 又上述撥水撥油性被膜，係使用矽系化合物或氟系化 合物來形成。 又上述砂系化合物是砂氧院’上述氟系化合物是氟院 基矽烷。 又上述高速用滾動軸承，係用來支承工作機械的主軸 的軸承。 又上述高速用滾動軸承，是斜角滾珠軸承或圓柱滾子 軸承。 本發明的高速軸承用潤滑油，由於在4〇。(：的動黏度爲 -10- 200848503 15 mm2/sec〜30 mm2/sec之基油中配合既定的脲系增稠劑 3重量7。以上9重量％未滿，即使是少量的潤滑油封入量， 仍可確保將該潤滑油封入內部之滾動軸承的耐荷重性，且 在高速旋轉下對軌道面供油的能力優異。 特別是脲系增稠劑的單胺成分，是相對於單胺全體含 有5 0莫耳％以上的選自脂肪族單胺及脂環式單胺中至少1 種單胺’增稠劑不容易被高速下的剪切力破壞，利用增稠 劑的毛細管現象，可穩定地將潤滑油的油分供應至滾道 面。 本發明之高速用滾動軸承，由於將上述潤滑油封入內 部，在負荷高離心力的狀態下，而不會流出軸承外，且能 長期間穩定地供應軸承潤滑所須的油量，又對高速下滑接 的軌道面，能形成潤滑所須厚度的油膜。因此能延長高速 旋轉下之軸承耐久壽命。 由於在軸承內環的滾道面表面、外環的滾道面表面、 轉動體的表面中至少一個，形成複數個微小凹部之凹坑 (dimple )，可提昇軌道環與轉動體的接觸面之油膜形成 能力，而能明顯提昇微量油供應狀態下之潤滑油壽命的延 長效果。 由於在選自軸承內環的外徑面、軸承外環的內徑面、 轉動體的表面中至少一個，藉由金屬鍍敷處理或磷酸被膜 處理來形成被膜，可大幅提昇該接觸面在微量油供應狀態 下之潤滑能力，而能明顯提昇微量油供應狀態下之潤滑油 壽命的延長效果。即使是從滾道部排除而堆積於周邊之潤 -11 - 200848503 滑油難以進行油供應的狀況，利用被膜效果，讓基油的擴 散變容易而提昇濕潤性，藉此可延長潤滑油壽命（燒 咬）。 由於在保持器的袋孔部內面具有凹部，保持於凹部內 的潤滑油，在軸承運轉時也會供應到轉動體與袋孔部內面 的接觸部，能使該接觸部的潤滑狀態保持良好。此外，由 於至少該凹部的緣部被去角，附著於轉動體表面之潤滑油 不容易被該緣部刮除，在袋孔部的必要部位容易取得潤滑 油。結果’能大幅延長在高速旋轉下的軸承耐久壽命。 由於在與上述潤滑油接觸的軸承內部表面的至少一部 分形成撥水撥油性被膜’即使在負荷高離心力的狀態下， 仍能使潤滑油的油分移動至滾道面，故潤滑油不會流出軸 承外，且能長期間穩定地供應軸承潤滑所須的油量，又對 高速下滑接的軌道面，能形成潤滑所須厚度的油膜。因此 能延長高速旋轉下之軸承耐久壽命。 【實施方式】 本發明之尚速用滾動軸承，構造上並沒有特別的限 制，例如是第1圖所示之斜角滾珠軸承。第1圖係封入潤 滑油的斜角滾珠軸承之縱截面圖。 該斜角滾珠軸承1，如第1圖所示，係將在內環2和 外環3之間用保持器5保持轉動體4所形成的軸承空間， 用固定於卡止槽（設於外環3的內周面）的密封構件6密 封而構成之斜角滾珠軸承。至少在轉動體4的周圍封入潤 -12- 200848503 滑油’在外環3的內徑面形成周槽狀的潤滑油袋孔7，以 物理性防止潤滑油的洩漏。由轉動體4和內環2及外環3 的接觸點連接成的直線，相對於徑方向具有接觸角石，其 可負荷徑荷重和一方向的軸荷重。轉動體4可由氮化矽、 碳化矽等的陶瓷製。在本發明，在內環2和外環3和轉動 體4所形成之軸承空間，封入後述本發明的高速軸承用潤 滑油8。 本發明的高速用滾動軸承的其他實施形態，是在選自 第1圖之內環的滾道面表面、外環的滾道面表面、轉動體 的表面中至少一個實施凹坑加工而構成之斜角滾珠軸承。 藉由凹坑加工，以在各表面形成微小凹部之凹坑。 關於凹坑加工’只要是能在軸承鋼構成的軌道環（內 環及外環）的滾道面表面或轉動體表面形成凹坑的方法即 可’可使用公知的方法。具體而言，可採用珠擊、缸桶硏 磨、雷射照射、蝕刻、模具轉印等等。其中，基於成本和 方便性的觀點，以使用珠擊法爲佳。 在本發明，爲了藉由珠擊來在軌道環的滾道面表面、 轉動體表面形成凹坑，例如是將粒徑30〜3 00 // m程度之 珠擊材朝軌道環的滾道面表面以〇.〇〗〜！ MPa的壓力噴射 1〜60秒，藉此形成凹坑。 作爲珠擊材，只要是可在軸承鋼構成之軌道環、轉動 體上形成凹坑者即可。具體而言，可列舉氧化鋁、碳化 矽、玻璃珠等等，其中，以使用經濟性和加工性優異之氧 化鋁爲佳。 -13- 200848503 藉由上述凹坑加工來在軌道環的滾道面表面、轉動體 表面形成的凹坑，從滾道面表面、轉動體表面起算的深度 宜爲0·1〜10/im，更佳爲1〜5#m。未達時，凹 坑效果變小故不佳。又若在5 # m以上，軸承的噪音變大 故不佳。 形成於軌道環的滾道面表面、轉動體表面的凹坑’爲 了使油膜厚度變穩定，較佳爲週期性地形成凹坑。該凹坑 較佳爲，朝與滾動滑動方向正交的方向延伸。藉此，從滾 道部排除而堆積於周邊之潤滑油’可更順利地進行油供 應。 本發明的高速用滾動軸承之其他實施形態，是在選自 第1圖之內環2的外徑面2 a、外環3的內徑面3 a、轉動 體4表面中至少一個形成被膜而構成之斜角滾珠軸承。這 些被膜，可對各面實施既定的表面處理來形成。表面處理 較佳爲，可減少轉動摩擦且不易剝離者。就潤滑性優異、 不容易剝離的表面處理而言，較佳爲金屬鑛敷處理或磷酸 被膜處理。 作爲金屬鍍敷處理，可使用電鍍、無電解鍍等的方 法。所使用的金屬較佳爲，C u、A g、N i、Z η、S η等的軟 質且與母材（軸承鋼）之密合性優異的金屬。 磷酸被膜處理，例如是將軌道環等浸漬於磷酸三酯溶 液中而在其等的表面形成磷酸金屬鹽被膜的處理。磷酸三 酯’是（R〇)3P = 0 (式中，R代表芳基、脂肪族烴基、脂環 族烴基）所代表的有機磷酸化合物，可使用市售工業用材 -14- 200848503 料之可塑劑等。作爲磷酸三酯，例如包括：磷酸三甲苯酯 (CH3C6H40)3P0、磷酸三苯酯（C6H5〇)3p〇、磷酸三丁酯 (C4H9〇)3PO等等。上述磷酸三酯，按照操作上的必要， 可用有機溶劑稀釋再使用。在讓磷酸三酯和軸承鋼反應而 在其表面形成金屬鹽被膜時，爲了提高反應速度只要邊加 溫邊進行即可，例如只要在6(TC左右浸漬1〜2小時即可 形成具有充分厚度的被膜。 藉由在後述的潤滑油中預先混入磷酸三酯，利用隨著 軸承的運轉所造成之溫度上昇，可在轉動體與內、外環的 接觸面形成磷酸金屬鹽被膜。本方法的好處在於，可隨時 補足被膜的摩耗。 本發明的高速用滾動軸承之其他實施形態，例如是用 保持器的袋孔部來保持轉動體，在該袋孔部的內面具有凹 部，至少該凹部的緣部被去角，藉此來構成斜角滾珠軸 承。第2圖係顯示這種斜角滾珠軸承之縱截面圖。第3圖 係斜角滾珠軸承1 1所使用的機械加工型保持器1 5的立體 圖。 該斜角滾珠軸承1 1，如第2圖所示，係將在內環i 2 和外環1 3之間用保持器1 5保持轉動體1 4所形成的軸承 空間，用固定於卡止槽（設於外環1 3的內周面）的密封 構件1 6密封而構成之斜角滾珠軸承。在內環1 2和外環！ 3 和轉動體1 4所形成之軸承空間’封入後述本發明的高速 軸承用潤滑油1 7。由轉動體1 4和內環1 2及外環1 3的接 觸點連接成的直線，相對於徑方向具有接觸角^ ’其可負 -15- 200848503 荷徑荷重和一方向的軸荷重。轉動體1 4可由氮化矽、碳 化矽等的陶瓷製。 如第3圖所示，在機械加工型保持器1 5的袋孔部內 面1 5a設置凹面狀的儲油部1 5c及離隙部1 5b。此外，對 設置該等凹部所產生的該凹部的緣部1 5 d實施去角加工。 儲油部1 5 c及離隙部1 5 b，僅設置任一方也可以。除該凹 部之緣部以外，也能在保持器之可能與轉動體接觸的所有 的緣部實施去角加工。 同樣的實施形態，例如是用保持器的袋孔部來保持轉 動體，在該袋孔部的內面具有凹部，至少該凹部的緣部被 去角，藉此來構成深槽滾珠軸承。第4圖係顯示這種封入 潤滑油之深槽滾珠軸承之縱截面圖。第5圖係深槽滾珠軸 承所使用的冠型保持器2 5的立體圖。 該深槽滾珠軸承2 1，如第4圖所示，係將在內環2 2 和外環23之間用保持器25保持轉動體24所形成的軸承 空間，用固定於卡止槽（設於外環2 3的內周面）的密封 構件2 6密封而構成之深槽滾珠軸承。在內環2 2和外環2 3 和轉動體24所形成之軸承空間，封入後述本發明的高速 軸承用潤滑油2 7。轉動體2 4可由氮化矽、碳化矽等的陶 瓷製。 如第5圖所示，在保持器2 5的袋孔部內面2 5 a設置 凹面狀的交叉面側儲油部2 5 b及底面側儲油部2 5 c，又對 δ又置該等凹部所產生之該凹部的緣部2 5 d實施去角加工。 除該凹部之緣部以外’也能在保持器之可能與轉動體接觸 -16- 200848503 的所有的緣部實施去角加工。 本發明之高速用滾動軸承中組裝的保持器，以樹脂製 爲佳。使用樹脂製保持器可謀求軸承的輕量化，而減輕高 速旋轉下的離心力的影響。又能抑制轉動體和保持器的滑 動部之摩擦發熱。 上述樹脂保持器，宜使用具備耐熱性及耐油性之樹 脂。例如可使用：PA樹脂、聚乙烯樹脂、聚縮醛樹脂、 聚對苯二甲酸乙二醇酯樹脂、聚對苯二甲酸丁二醇酯樹 脂、聚碳酸酯樹脂、聚苯硫樹脂、聚醚颯樹脂、酚樹脂、 聚醚醯亞胺樹脂、聚醯胺醯亞胺樹脂、PEEK樹脂、熱塑 性聚醯亞胺樹脂等等。這些可單獨或組合2種以上來使 用。 其等中，基於輕量、和油的親和性優異、機械穩定性 優異等的觀點，較佳爲·· PA46樹脂、PA66樹脂、PA9T 樹脂等經玻璃纖維等強化的 PA樹脂，或是電木 (Bakelite)等的酚樹月旨、PEEK樹月旨。 本發明的高速用滾動軸承的其他實施形態，例如第6 圖〜第9圖所示，是在與封入的潤滑油接觸之軸承內部表 面之至少一部分形成撥水撥油性被膜之斜角滾珠軸承。 針對即使是較少的潤滑油封入量仍能充分對應於高速 旋轉，且可謀求工作機械的緊致化和運轉經費的降低之高 速用滾動軸承，進行深入探討的結果發現，在高速用滾動 軸承的構件之軸承內部表面的至少一部分設置撥水撥油性 被膜，並封入既定的潤滑油，可獲得高速使用時的壽命長 -17- 200848503 之滾動軸承。 在與潤滑劑（封入軸承之潤滑油等）接觸之軸承內部 表面的至少一部分形成撥水撥油性被膜，利用撥水撥油性 被膜的表面張力能防止潤滑劑留在被膜表面而使其活潑地 移動。因此，活潑移動之既定潤滑劑會持續存在轉動面和 滾道面等的滑動表面，而能提昇潤滑作用的持續性以獲得 長壽命的滾動軸承。 第6圖係斜角滾珠軸承的撥水撥油性被膜的形成位置 一例之截面圖。撥水撥油性被膜，只要形成在與潤滑油3 7 接觸之軸承內部表面的至少一部分即可，更佳爲形成在滑 動表面以外。在此的滑動表面是包括：內環軌道面32a、 外環軌道面3 3 a、保持器3 5與轉動體3 4的接觸面、轉動 體34的表面等等。 第6圖之斜角滾珠軸承3 1，係將在內環3 2和外環3 3 之間用保持器3 5保持轉動體3 4所形成的軸承空間，用固 定於卡止槽（g受於外環3 3的內周面）的密封構件3 6密 封’且在密封構件3 6之軸承內部側表面的一部分形成撥 水撥油性被膜3 8 a。在內環3 2和外環3 3和轉動體3 4所形 成之軸承空間，封入後述本發明的高速軸承用潤滑油3 7。 由轉動體3 4和內環3 2及外環3 3的接觸點連接成的 直線，相對於徑方向具有接觸角/3，其可負荷徑荷重和一 方向的軸荷重。又轉動體3 4可由氮化矽、碳化矽等的陶 瓷製。 第7圖〜第9圖是上述撥水撥油性被膜的形成位置的 -18- 200848503 其他例之截面圖。第7圖，是在外環之除軌道面3 3 a以外 的內徑面、密封構件3 6的軸承內部側表面形成撥水撥油 性被膜38b ;第8圖，是在內環之除軌道面32a以外的外 徑面、密封構件3 6的軸承內部側表面形成撥水撥油性被 膜3 8 c ;第9圖，是在除了與轉動體3 4的接觸面以外之保 持器3 5的表面形成撥水撥油性被膜3 8d。第7圖〜第9圖 中除了撥水撥油性被膜以外的構造是和第6圖相同。 第6圖〜第9圖雖是個別顯示撥水撥油性被膜的形成 位置，但這些形成位置可單獨使用或組合2個以上來使 用。 又關於同樣的實施形態，例如第1 0圖〜第1 3圖係顯 不，在與封入的潤滑油接觸之軸承內部表面的至少一部分 形成撥水撥油性被膜之深槽滾珠軸承。 第1 〇圖係顯示深槽滾珠軸承之撥水撥油性被膜的形 成位置一例之截面圖。撥水撥油性被膜，只要形成於與潤 滑油47接觸之軸承內部表面的至少一部分即可，更佳爲 形成在滑動表面以外。在此的滑動表面是包括：內環軌道 面42a、外環軌道面43a、保持器45與轉動體44的接觸 面、轉動體44的表面等等。 第1 0圖之深槽滾珠軸承4 1，係將在內環42和外環 43之間用保持器45保持轉動體44所形成的軸承空間，用 固定於卡止槽（設於外環4 3的內周面）的密封構件4 6密 封’且在密封構件46之軸承內部側表面的一部分形成撥 水撥油性被膜4 8 a。在內環4 2和外環4 3和轉動體4 4所形 -19- 47 ° 200848503 成之軸承空間，封入後述本發明的高速軸承用潤滑油 又轉動體44可由氮化矽、碳化矽等的陶瓷製。 第1 1圖〜第1 3圖是上述撥水撥油性被膜的形成 的其他例之截面圖。第1 1圖，是在外環之除軌道面 以外的內徑面、密封構件4 6的軸承內部側表面形成 撥油性被膜48b ;第12圖，是在內環之除軌道面42a 的外徑面、密封構件4 6的軸承內部側表面形成撥水 性被膜48c ;第13圖，是在除了與轉動體44的接觸 外之保持器4 5的表面形成撥水撥油性被膜4 8 d。第： 〜第1 3圖中，除了撥水撥油性被膜以外的其他構造 第1 0圖相同。 第1 0圖〜第1 3圖雖是個別顯示撥水撥油性被膜 成位置，但這些形成位置可單獨使用或組合2個以上 用。 藉由將撥水撥油性被膜38a〜38d、48a〜4 8d如 圖〜第1 3圖所示形成於軸承內部表面，利用撥水撥 被膜38a〜3 8d、48a〜48d的表面張力，能避免被封 潤滑油37、47留在該被膜表面而使其能活潑地移動 此，例如在未形成該等被膜38a〜3 8d、48a〜48d之 軌道面32a、42a、外環軌道面33a、43a、保持器3ί 與轉動體34、44的接觸面、轉動體34、44的表面等 會繼續地供應潤滑油3 7、47，藉此提昇潤滑作用的持 而成爲長壽命的滾動軸承。 此外，藉由在滑動表面以外形成撥水撥油性被膜 位置 43a 撥水 以外 撥油 面以 1圖 是和 的形 來使 第6 油性 入的 。因 內環 、45 等， 續性 ，可 -20- 200848503 避免滑接所造成之該被膜的剝離。 形成撥水撥油性被膜所使用的材料，可 系之撥水撥油劑，並沒有特別的限定。撥水 佳爲：矽烷氧等的矽系撥水撥油劑構成的被 氟烷基矽烷來形成之撥水撥油性被膜。 就市售品而言，例如包括：日 (Mektron )製：諾庫斯加德ST-420，大金 達因，信越化學製：全氟烷基矽烷KBM7803 本發明的高速用滾動軸承之上述實施形 潤滑油接觸之軸承的內部表面形成撥水撥油 被膜的形成方法並沒有特別的限定。爲了在 之軸承的內部表面形成撥水撥油性被膜，可 漬於砂院氧等的砂系撥水撥油劑的分散液中 成撥水撥油性被膜。又可採用：真空蒸翁 (PVD )、化學蒸鍍（CVD )、離子鍍等的 是電鍍等等。 也能使用市售的撥水撥油劑，塗布於與 軸承內部表面來形成撥水撥油性被膜。其中 各零件分別進行撥水撥油處理、加工成本有 較佳爲採用將滾動軸承浸漬於撥水撥油劑： 法。 本發明之高速用滾動軸承，較佳爲封入 容積之1體積％以上1 〇體積％未滿之潤滑油 積％，潤滑所須的潤滑油量不足，容易發生右 使用砂系、氟 撥油性被膜較 膜，或是使用 本美可多能 工業製：優利 等等。 態，只要在與 性被膜即可， 與潤滑油接觸 將滾動軸承浸 ，經乾燥而形 I、物理蒸鍍 乾式鍍敷，或 潤滑油接觸的 ，基於不須對 利等的觀點， 汗散液中的方 軸承容積部的 。若未達1體 与竭。若在1 〇 -21 - 200848503 體積％以上，攬拌轉矩變大，發熱變大，不僅無法延長潤 滑壽命，且成本增加，又對環境而言也不佳。 本發明之高速用滾動軸承，除上述各實施形態所示之 斜角滾珠軸承及深槽滾珠軸承以外，也能使用圓柱滾子軸 承、圓錐滾子軸承、自動調心滾子軸承、針狀滾子軸承、 止推圓柱滾子軸承、止推圓錐滾子軸承、止推針狀滾子軸 承、止推自動調心滾子軸承等等。其等當中，基於同時具 備高速旋轉的旋轉精度和耐荷重性能雙方的觀點，較佳爲 使用斜角滾珠軸承或圓柱滾子軸承。 本發明之高速用滾動軸承，其特徵在於：係使用含有 以下的基油和脲系增稠劑而構成之高速軸承用潤滑油。 本發明的基油，可使用40°C的動黏度（以下簡稱動黏 度）爲15〜30 mm2/Sec的潤滑油。較佳爲動黏度15〜25 mm2/sec的潤滑油。在動黏度未達1 5 mm2/sec的情形，黏 度過低而無法獲得充分的耐負荷性。又在動黏度超過3 0 mm2/seC的情形，在高速旋轉下供應至軌道面的油量不 足，會造成軸承壽命提早結束。 上述潤滑油的種類，較佳爲合成烴油、酯油、烷基二 苯醚油、或是該等的混合油。 又較佳爲，合成烴油、酯油、烷基二苯醚油各個的動 黏度都在1 5〜30 mm2/sec。若位於此範圍，即使是成爲混 合油的情形’也能確保動黏度的範圍在1 5〜3 0 m m2 / s e c。 在成爲混合油的情形，較佳爲合成烴油和酯油的混合 油。混合比例較佳爲，合成烴油/酯油（重量比）=8/2〜 •22- 200848503 2/8。更佳爲合成烴油的重量比例爲酯油之同量以上。 此外，也能單獨使用烷基二苯醚油。 就合成烴油而言，例如包括：正石蠟、異石爆、 烯、聚異丁烯、1-癸烯寡聚物、卜癸烯和乙烯之共寡 等等的聚-α -烯烴等等。 就酯油而言，例如包括：二丁基癸二酸醋、二-2 · 己基癸二酸酯、二辛基己二酸酯、二異癸基己二酸酯 十三烷基己二酸酯、雙十三烷酯、甲基·乙醯基二壬 的二酯油；三辛基偏苯三酸酯、十三烷基偏苯三酸酯 辛基均苯四甲酸酯等的芳香族酯油；三羥甲基丙烷 酯、三羥甲基丙烷壬酸酯、季戊四醇-2_乙基己酸酯、 四醇壬酸酯等的多元醇酯油、碳酸酯油等等。 就烷基二苯醚油而言，例如包括：單烷基二苯醚 烷基二苯醚、聚烷基二苯醚等等。 本發明的高速軸承用潤滑油所使用的基油，表面 爲25 mN/m以上，較佳爲27〜40 mN/m，且密度爲 g/cm3以下，較佳爲0.8〜0.93 g/cm3。若表面張力未: mN/m，不容易利用毛細管現象來移動至滾道部，無 定供應高速下所須的油量，若密度超過0.95 g/cm3， 地不容易利用毛細管現象來移動至滾道部，無法穩定 高速下所須的油量。 本發明的高速軸承用潤滑油所使用的脲系增稠劑 讓聚異氰酸酯成分和單胺成分進行反應而製得。 就聚異氰酸酯成分而言，例如包括：對苯二異 聚丁 聚物 乙基 、雙 酯等 、四 辛酸 季戊 張力 0.95 t 25 法穩 同樣 供應 ，係 氰酸 -23- 200848503 酯、甲苯二異氰酸酯、二苯二異氰酸酯、二苯甲烷二異氰 酸酯、十八烷基二異氰酸酯、癸基二異氰酸酯、己烷二異 氰酸肖曰等等。其等中，較佳爲芳香族二異氰酸酯。 此外’也能使用二胺和莫耳比過剩之二異氰酸酯反應 所得之聚異氰酸酯。作爲二胺可列舉：乙二胺、丙二胺、 丁一胺、己一胺、辛二胺、苯二胺、甲苯二胺、二甲苯二 胺、二胺基二苯基甲烷等等。 單胺成分，相對於單胺全體，是含有選自脂肪族單胺 及脂環式單胺中至少1種單胺5 0莫耳％以上，較佳爲含有 80莫耳％以上。藉由含有50莫耳〇/。以上，增稠劑不容易被 高速下的剪切力破壞，利用增稠劑纖維的毛細管現象，可 穩定地將潤滑劑中的油分供應至滾道面。 就脂肪族單胺及脂環式單胺以外的單胺而言，例如爲 芳香族單胺。 就脂肪族單胺而言，可列舉己胺、辛胺、十二烷胺、 十六烷胺、十八烷胺、硬脂胺、油胺等等，其中較佳爲十 八烷胺。 就脂環式單胺而言，例如爲環己胺等等。 就芳香族胺而言，可列舉苯胺、對甲苯胺等等，其中 較佳爲對甲苯胺。 本發明之脲系增稠劑，相對於潤滑油全體，其含量爲 3重量。/。以上9重量％未滿，較佳爲5重量％以上9重量％ 未滿。配合量未達3重量％時’基油保持能力不足’特別 是在旋轉初期，暫時會有大量的油分分離而發生潤滑油的 -24- 200848503 洩漏，如此會造成軸承耐久壽命變短。又若配合量超過9 重量％，基油的相對含量變少，油供應性變差，會提早陷 入潤滑不足而同樣地造成軸承耐久壽命變短。 又在本發明的高速軸承用潤滑油中，按照需要可含有 公知的潤滑油用添加劑。作爲該添加劑，例如包括：有機 鋅化合物、胺系、酚系化合物等的氧化防止劑；苯並三唑 等的金屬減活劑；聚甲基丙烯酸酯、聚苯乙烯等的黏度指 數提昇劑；二硫化鉬、石墨等的固體潤滑劑；金屬磺酸 鹽、多元醇酯等的防銹劑；有機鉬等的減摩擦劑；酯、醇 等的油性劑；磷系化合物等的摩耗防止劑等等。這些可單 獨或組合2種以上來添加。添加劑的含量較佳爲，個別佔 潤滑油全量的〇.〇5重量％以上，合計量佔潤滑油全量的 0.1 5〜1 0重量％的範圍。在合計量超過1 0重量％時，不僅 無法期待隨著含量增多的效果，且其他成分的相對含量變 少，可能在潤滑油中發生添加劑的凝聚，而造成轉矩上昇 等的不理想現象。 近年來，在AC馬達、DC馬達等的汎用馬達方面，隨 著馬達的小型化的進展，軸承有在更高速、更高面壓下運 轉的傾向。習知之使用鋰皂等的金屬皂潤滑油的方式，無 法獲得充分的耐久性，而有使用耐久性更優異的脲系潤滑 油的趨勢。相對於與汽車引擎直接相關的電氣輔助設備所 使用的馬達的使用溫度爲1 5 0 °C以上；換氣扇用馬達、燃 料電池用鼓風機馬達、空氣清淨器馬達、風扇馬達、伺服 馬達、步進馬達等的產業機械用或資訊機器用的馬達，汽 -25- 200848503 車的起動馬達、電動方向盤馬達、方向調整用俯仰操縱馬 達、雨刷馬達、電動窗馬達等的電氣機器用馬達的使用溫 度’大多爲未達1 5 0 t之較低溫。在這種較低溫的使用環 境下’習知的脲系潤滑油之基油的流動性不佳，在要求更 高速化的情形’供應給滾道面的基油不足，而存在著容易 發生潤滑不良的問題。 將本發明之高速軸承用潤滑油封入其中之高速用滾動 軸承’即使是在上述較低溫下而要求高速化的環境下，仍 具有優異的滾道面的油供應性，就算是對於上述的換氣扇 用馬達、燃料電池用鼓風機馬達、空氣清淨器馬達、風扇 馬達、伺服馬達、步進馬達等的產業機械用或資訊機器用 的馬達’汽車的起動馬達、電動方向盤馬達、方向調整用 俯仰操縱馬達、雨刷馬達、電動窗馬達等的電氣機器用馬 達，也都能良好地適用。 實施例 以下用試驗例來進一步說明本發明，但本發明並不限 於此。各實施例及比較例所使用的基油密度（1 5 °C )及動 黏度（40°C )的資料顯示於表1〜表5。表1〜表5所示的 稠度是根據ns K2220 5.3所測定之60次混合稠度；又25 °C之基油的表面張力，是用Du Nouy環式簡易表面張力計 所測得的測定値。表1〜表5所示的離心離油度，係用以 下的離心油分離試驗所測得的値。 -26- 200848503 &lt;離心油分離試驗&gt; 使用離心分離機，將5 0g的潤滑油試料放入離心分離 管，以4(TC、2 3 000 G的加速度進行離心分離7小時，依 下式求出離心油離度。 (離心油離度％ ) = ( 1 -試驗則的增f周劑濃度/試驗後 的增稠劑濃度）X 1 0 0 實施例1〜實施例5、比較例1、比較例2及比較例5 在表1所示的基油的一半量中，依表1所示的比例溶 入4，4’-二苯基甲烷二異氰酸酯（日本聚氨酯工業製，密 利歐最特Μ T，以下稱M DI )，在剩下一半的基油中，溶 入MD12倍當量的單胺。各個的配合比例及種類如表1所 示0 邊將溶入M DI的溶液攪拌，邊將溶入單胺的溶液加 入後’以100〜120 °C持續攪拌30分鐘以進行反應，藉此 在基油中生成二脲化合物而製得潤滑油試料。所使用的基 油密度、動黏度、表面張力的測定結果顯示於表1。測定 所製得的潤滑油試料之稠度及離心離油度。又進行以下所 示的常溫高速潤滑油試驗，測定常溫高速潤滑油壽命時 間。測定結果整理於表1。 &lt;常溫高速潤滑油試驗-深槽滾珠軸承（6204 ) &gt; 將潤滑油試料0 . 1 4g (軸承全空間容積的約3體積 % )對準滾道面而封入深槽滾珠軸承（6204 )，實施非接 -27- 200848503 觸密封而作成各個試驗軸承。讓試驗軸承負荷軸荷重 6 70N和徑荷重67N，在常溫環境下以1 5 000 rpm的旋轉速 度旋轉，測定迄燒咬發生爲止的時間作爲潤滑油壽命時 間。該耐久試驗中，軸承的節圓直徑dm ( mm )和轉數N (rpm )的乘積（dmN値）爲52萬。 比較例3及比較例4 將基油和硬脂酸鋰以表1所示的比例配合而製得潤滑 油試料。對於所使用的基油和潤滑油試料，係測定和實施 例1同樣的項目。結果整理於表1。 &lt;常溫高速滾珠軸承試驗-斜角滾珠軸承&gt; 將實施例1、實施例2、實施例5、比較例1〜比較例 3或比較例5的潤滑油試料3.0 g (軸承全容積的約1 0 %體 積）對準滾道面而封入斜角滾珠軸承（外徑1 5 0 m m X內徑 100 mm，內外環SUJ2，轉動體13/32吋的氮化矽球）， 實施非接觸密封而作成各個試驗軸承。在對試驗軸承用 1 ·8 GPa的定壓加壓下，藉由外筒冷卻將軸承冷卻以使軸 承外環保持在50°C以下，並以1 45 00 rpm的旋轉速度進行 方定轉°測定迄燒咬發生爲止的時間作爲潤滑油壽命時間。 读耐久試驗中，軸承的節圓直徑 dm ( mm )和轉數 N (rpm )的乘積（dmN値）爲1 85萬。 -28- 200848503 [表l] 實施例 :匕較1 列 1 2 3 4 5 1 2 3 4 5 潤滑油配合(重量％) 基油 合成烴油n - - - - - 94.9 - - - - 合成烴油2) 62 47.5 46.5 60 - - - 46 - 57 酯油3) 33 47.4 46.5 32 一 - - 46 - 31 酯油4) 93 烷基二苯基醚油5) - - - - 93 - - - - - 矽酮油6) 80 - 基油密度(g/cm3) 0.86 0.88 0.88 0.86 0.93 0.8 0.99 0.88 0.95 0.86 4〇°C的基油動黏度(_2/sec) 23 19 19 23 22 5 53 19 16 22 25°C的基油表面張力（mN/m) 31.5 30.5 30.5 31.5 35.4 28.1 33.7 30.5 22.7 31.5 增稠劑 硬脂酸鋰 8 20 單胺:辛胺 2.5 1.8 2.8 — 2.8 1.8 2.8 - - 6.1 單胺:環己胺 — 0.7 一 3.5 一 0.7 - 一 一 - 單胺:對甲苯胺 - - 0.6 — 0.6 - 0.6 - - - 二異氰酸酯：mdi7) 2.5 2.6 3.6 4.5 3.6 2.6 3.6 - - 5.9 (潤滑油配合合計） 98 100 100 100 100 100 100 100 100 100 稠度 300 290 290 270 290 320 280 290 280 260 離心離油度％ 28 24 18 16 20 33 12 38 41 7 常溫高速潤滑油壽命h 6204 軸承，dmN=52 萬 &gt;1500 &gt;1500 &gt;1500 1250 &gt;1500 270 320 110 40 640_ 斜角滾珠軸承,dmN=185萬 &gt;1000 &gt;1000 - - &gt;1000 190 260 50 - 320_ 1) 密度0.80 g/cm3 ’ 40°C動黏度5 _2/sec，新日鐵化學製，新福路特2012) f度0.83 g/cm3，40°C動黏度30 mm2/SeC，新日鐵化學製，新福路特601 3 ) f度0.92 g/cm3，40°C動黏度12 mm2/SeC，汽巴特殊化學品製，雷歐路普DOS4) 密度0.99 g/cm3 ’ 4(rc動黏度53 mm2/sec，汽巴特殊化學品製，雷歐路普 LPE602 5) 密度0.93 g/cm3，4〇。(：動黏度22 mm2/Sec，松村石油硏究所製，摩列斯科哈依路 普 LB226 )密度 0.95 g/cm3，4(TC 動黏度 16 mm2/Sec，東麗道康寧製，SH200 (20 )7)日本聚氨酯工業製，密利歐聶特]^丁 -29- 200848503 由表1可知，本發明所使用的潤滑油較佳爲：（1 ) 在40C的動黏度爲15 mm2/sec〜30 mm2/sec的基油中， 含有3重量％以上9重量％未滿之脲系增稠劑；（2 )脲系 增稠劑的單胺成分，是相對於單胺全體含有5〇莫耳％以上 的選自脂肪族單胺及脂環式單胺中至少1種單胺之單胺成 分；（3)基油的表面張力爲25 mN/m以上，且密度爲 0.95 g/cm3以下；基油係合成烴油、酯油、烷基二苯醚油 或其等的混合油。 實施例6〜實施例9、比較例8 在表2所示的基油的一半量中，依表2所示的比例溶 入MDI，在剩下一半的基油中，溶入MDI2倍當量的單 胺。各個的配合比例及種類如表2所示。 邊將溶入MDI的溶液攪拌，邊將溶入單胺的溶液加 入後，以1 0 0〜1 2 0 °C持續攪拌3 0分鐘以進行反應，藉此 在基油中生成二脲化合物而製得潤滑油試料。所使用的基 油密度、動黏度、表面張力的測定結果顯示於表2。測定 所製得的潤滑油試料之稠度及離心離油度。又進行以下所 示的常溫高速潤滑油試驗’測定常溫高速潤滑油壽命時 間。測定結果整理於表2。 &lt;常溫高速潤滑油試驗-深槽滾珠軸承（6204 ) &gt; 藉由珠擊法，用粒度#1〇〇(粒徑106〜i49//m)的氧 化鋁以0.2 MPa的壓力噴射約20秒於深槽滾珠軸承 -30- 200848503 (62 04 )的外環軌道面，以在外環軌道面實施深2〜3 μ m 的凹坑加工，如此製作成試驗軸承。 將潤滑油試料〇 . 〇 2 3 5 g (軸承全空間容積的約〇 . 5體 積％ )對準滾道面而封入該試驗軸承，實施非接觸密封而 作成各個試驗軸承。讓試驗軸承負荷軸荷重6 7 0N和徑荷 重6 7N，在常溫環境下以1 0000 rpm的旋轉速度旋轉，測 定迄燒咬發生爲止的時間作爲潤滑油壽命時間。該耐久試 驗中，軸承的節圓直徑dm ( mm )和轉數N ( rpm )的乘 積（dmN値）爲35萬。 比較例6〜比較例7 將基油和硬脂酸鋰以表2所示的比例配合而製得潤滑 油試料。對於所使用的基油和潤滑油試料，係測定和實施 例6同樣的項目。結果整理於表2。 &lt;常溫高速潤滑油試驗-斜角滾珠軸承&gt; 藉由珠擊法，用粒度#100 (粒徑106〜149&quot; m)的氧 化錦以0.2 MPa的壓力噴射約20秒於斜角滾珠軸承（外 徑150 mmx內徑100 mm，內外環SUJ2 ’轉動體13/32吋 的氮化矽球）的外環軌道面，以在外環軌道面實施深2〜3 A m的凹坑加工，如此製作成試驗軸承。 將實施例6〜9、比較例6〜8的潤滑油試料3.0g (軸 承全容積的約1 0%體積）對準滾道面而封入該試驗軸承， 貫施非接觸密封而作成各個試驗軸承。在對試驗軸承用 -31 - 200848503 1 . 8 G P a 的 承外環保持 旋轉。測定 該耐久試1 (rpm )的， 2 〇 € B力卩®下’藉由外筒冷卻將軸承冷卻以使軸 在50C以下，並以M5〇() ”爪的旋轉速度進行 迄燒咬發生爲止的時間作爲潤滑油壽命時間。 $中，軸承的節圓直徑dm ( mm )和轉數N 尾積（dmN値）爲185萬。測定結果整理於表 -32- 200848503 [表2] 實施例 比較例 6 7 8 9 6 7 8 潤滑油配合(重量％) 基油 合成烴油]) 62.5 46.5 60 46 46 57 酯油2) 33 46.5 一 32 46 46 31 烷基二苯基醚油3) — - 93 - - - - 基油密度(g/cm3) 0.86 0.88 0.93 0.86 0.88 0.88 0.86 40°C的基油動黏度(mm2/sec) 23 19 22 23 19 19 22 25t：的基油表面張力(mN/m) 31.5 30.5 35.4 31.5 30.5 30.5 31.5 增稠劑 硬脂酸鋰 8 8 單胺:辛胺 2.5 2.8 2.8 - - - 6.1 單胺:環己胺 一 - — 3.5 一 - - 單胺:對甲苯胺 — 0.6 0.6 - - - - 二異氰酸酯:mdi4) 2.5 3.6 3.6 4.5 - — 5.9 (潤滑油配合合計） 100 100 100 100 100 100 100 稠度 300 290 290 270 290 290 260 離心離油度％ 28 18 20 16 38 38 7 珠擊 有 有 有 有 有 並 j\\\ te jw\ 常溫高速潤滑油壽命h 6204 軸承，dmN=35 萬 &gt;2000 &gt;2000 &gt;2000 &gt;2000 470 210 550 斜角滾珠軸承，dmN=185萬 - &gt;2000 - - 220 50 320 1) 密度0.83 g/cm3，40°C動黏度30 mm2/Sec，新日鐵化學製，新福路特601200848503 IX. OBJECT OF THE INVENTION [Technical Field] The present invention relates to a high-speed bearing lubricating oil used for a rolling bearing for supporting a working shaft of a working machine spindle (spjnd丨e), and a high-speed lubricating oil sealed therein Rolling bearings [Prior technology] The main shaft of the working machine, in order to improve the processing efficiency, must be rotated at high speed. Main lubrication methods for high-speed rotation, including oil mist lubrication, oil and gas lubrication, and injection lubrication methods. However, 'these lubrication methods, due to the need to install additional equipment such as compressed air and supply, will result in higher cost of operation and operation of the working machine.' In contrast, lubricating oil lubrication is better because of the necessity of maintenance. Lubrication method. For example, in the case of a high-speed rolling bearing for supporting a rotating shaft rotating at 200 rpm or higher, an angular ball bearing cylindrical roller bearing for supporting a spindle of a working machine, and the like are included. The angled ball bearing 51 shown in Fig. 14 is a straight line connecting the steel ball 54 and the inner ring 52 and the outer contact point, in addition to the radial direction, except for the load of the load of the load of the load. It has an angle (angle) α. Lubricating oil is enclosed in the inner ring 52 and the outer ring 5 3 and the steel ball 5 4 are formed. It is composed of a beveled bead bearing, a cylindrical roller bearing, etc., and the oil, the shaft, etc. are low in cost, and the 8000 is the bearing, and also the 1 53 contact air bearing speed - 5 - 200848503 rolling bearing The lubricant to be used is preferably a lubricant which is not required to be repaired by oil supply or the like and whose consistency is adjusted so as not to pollute the surrounding environment. The lubrication characteristics and problems required for the lubricating oil used for high-speed rolling bearings such as rolling bearings for spindles can be arranged as follows. (a) In order to maximize the lubrication life of long-life rolling bearings, as explained in (i) to (iii) below, it must be met: lubricants (lubricants or their base oils) are not easily leaked from the rolling bearings, and the heat resistance of the lubricating oil is excellent. It can form the requirements of the oil film thickness required for lubrication. (i) When the rolling bearing is running at a high speed, the centrifugal force causes the lubricating oil in the rolling bearing to flow to the outside of the bearing, or separates and drains the base oil in the lubricating oil, and is not easily left in the vicinity of the raceway surface to be lubricated, so that it is easy to occur Poor lubrication. In order to prevent such a situation from occurring, a countermeasure is to mount a plate member such as a sealing plate on a rolling bearing. However, depending on the construction of the bearing, it may happen that the installation cannot be performed, and even if the sealing member is installed, it may occur that the lubricant or the lubricating oil cannot be completely sealed. In the case of a non-high-speed rolling bearing, excess lubricating oil extruded from the friction portion due to the movement of the rotating body or the retainer is recirculated to the inside of the bearing to a certain extent under the condition of rotation to be relubricated. However, in the rolling bearing for the shaft supporting such as a working machine that rotates at a high speed, since the wind pressure generated in the inner portion of the bearing hinders the progress of the recirculation, it is difficult to supply the lubricating oil to the race portion, and the lubricating failure is likely to occur. Therefore, in a rolling bearing that rotates at a high speed, only a small amount of lubricating oil is used for lubrication, so the nature of the lubricating oil is particularly important. Lubricating oils used in high-speed rolling bearings must be required to maintain lubrication even with a small amount of lubricating oil. -6 - 200848503 (i i) When the operating conditions are increased, the rolling surface of the bearing is heated to a high temperature. In this case, the lubricating oil with poor heat resistance generates heat, which significantly shortens the life of the lubricating oil. In response to this problem, attempts have been made to obtain a heat-resistant thickener or base oil, or to add an oxidation preventive agent, to achieve satisfactory durability improvement. (ni) The conventional lubricating base oil which improves the lubricity (oil film thickness) has a high viscosity, and the shear friction resistance becomes large, which causes an increase in torque. In order to suppress these phenomena, the viscosity of the base oil is lowered. The temperature associated with high-speed operation increases and becomes a low-viscosity lubrication thinning, which may cause sliding wear. (b) Lubricating oil for bearings with low torque (temperature rise suppression), although the base oil viscosity can be reduced at high speed as described above, the temperature rise will cause a significant decrease in viscosity, and the thickness required for lubrication Oil film. (c) Regarding low-vibration lubricating oil, the vibration of the bearing may increase due to the thickener. That is, in the case where the thickener contained is a hard agglomerated lubricating oil, the lubricated rolling bearing becomes large. This conventional lubricating oil is used in a high-speed rolling type and does not meet the requirements of long life, low torque, and physical properties of the bearing. As a countermeasure against this, in addition to the proposal of a urea compound (see Patent Document 1 to Patent Document 3), it is not sufficient to obtain a higher speed performance. For example, the lubricating oil composition disclosed in Patent Document 3 is partially deteriorated and tried to be used. However, if the lubricating oil is large and hot, the oil film may be high, but the shaft may not be shaped. It is possible to form a large vibration and the lubricating oil consumption of the bearing is changed to include: 40 -7- 200848503 °C The dynamic viscosity of the base oil is 15 mm 2 /sec or more and 40 mm 2 /sec or less. A thickener of a diurea compound in an amount of 9% by mass or more and 14% by mass or less of the entire composition, and a mixed consistency of 2 2 or more and 3 2 or less. However, in the above lubricating oil composition, it is also difficult to reduce the blending amount of the thickener to reduce the amount of lubricating oil enclosed, and it is not sufficient to correspond to the high-speed rotation of the bearing, and it is necessary to achieve compaction of the working machine and operation cost. It will be difficult to lower. In addition, in recent years, the use of rolling bearings has become more and more severe, and the spindle used for high-speed rotation in which the product of the pitch diameter dm (mm) and the number of revolutions N (rpm) (dmN値) is 17 million or more. Rolling bearings and the like have also increased. With such a high speed of rotation of the bearing, it is quite difficult for the existing lubricating oil to fully conform to the required performance of the bearing. Patent Document 1: JP-A-2000-169872 (Patent Document 2) Japanese Laid-Open Patent Publication No. JP-A No. Hei. The purpose of the present invention is to provide a high-speed bearing lubricating oil that can be used for a rolling bearing, which can correspond to, for example, a product of a pitch diameter dm (mm) and a number of revolutions N (rpm) even with a small amount of lubricating oil. (dmN値) is a high-speed rotation of 丨70 million or more, and it is possible to reduce the workmanship and the like, and to reduce the operation cost. Further, a high-speed rolling bearing for sealing the lubricating oil inside is provided. The lubricating oil for a local speed bearing of the present invention is characterized in that it contains a base-8-200848503 oil and a urea thickener, and the dynamic viscosity of the base oil at 40 ° C is 15 mm 2 /sec to 30 mm 2 / The sec, the urea-based thickener is obtained by reacting a polyisocyanate component and a monoamine component; the monoamine component contains 50 mol% or more of an aliphatic monoamine and an alicyclic ring with respect to the entire monoamine. The monoamine component of at least one monoamine of the monoamine; and the content of the urea thickener is not more than 3% by weight to 9% by weight based on the total amount of the lubricating oil. Further, the base oil has a surface tension of 25 mN/m or more and a density of 0. 95 g/cm3 or less. Further, the base oil is at least one selected from the group consisting of synthetic hydrocarbon oils, ester oils, and alkyl diphenyl ether oils. The high-speed rolling bearing according to the present invention is a high-speed rolling bearing for supporting a shaft that rotates at a high speed, and is characterized in that the rolling bearing has: an inner ring and an outer ring, and a plurality of rotating bodies interposed between the inner ring and the outer ring. a retaining member for holding the rotor, a sealing member for covering an opening between the inner ring and the outer ring; and lubricating oil surrounding the rotating body, the lubricating oil using the high speed bearing of the present invention Use lubricating oil. Further, at least one of the surface of the raceway surface selected from the inner ring, the surface of the raceway surface of the outer ring, and the surface of the rotor is subjected to pit processing. Further, the pits are processed by beading, and the pits formed on the respective surfaces by the processing are from the surface to a depth of 〇·1 to 1 〇#m ° and are selected from the outer diameter surface of the inner ring. At least one of the inner diameter surface of the outer ring and the surface of the rotor forms a film. Further, the above-mentioned film is a film formed by metal plating treatment or phosphoric acid film treatment -9·200848503. Further, the holder has a concave portion on the inner surface of the pocket and at least the edge portion of the concave portion is chamfered. Further, the concave portion is an oil storage portion or a relief portion. Further, the above holder is a resin holder. Further, the resin used in the above retainer is a polyamide (hereinafter referred to as PA) resin, a phenol resin or a polyetheretherketone (hereinafter referred to as PEEK) resin. Further, at least a part of the inner surface of the bearing which is in contact with the lubricating oil forms a water-repellent oil-repellent coating. Further, the water-repellent oil-repellent coating film is formed of: (1) a part of the inner side surface of the bearing of the sealing member, (2) an inner diameter surface other than the rail surface of the outer ring, and a bearing inner side surface of the sealing member, (3) at least one of an outer diameter surface of the inner ring other than the orbital surface and a bearing inner side surface of the sealing member, and (4) a surface of the retainer other than the contact surface with the rotating body.  One. Further, the above-mentioned water-repellent oil-repellent film is formed using a lanthanoid compound or a fluorine-based compound. Further, the above sand-based compound is a sand-oxygen institute. The fluorine-based compound is a fluorine-based decane. Further, the above-described high speed rolling bearing is a bearing for supporting a main shaft of a working machine. Further, the above high speed rolling bearing is a bevel ball bearing or a cylindrical roller bearing. The lubricating oil for high-speed bearings of the present invention is at 4 〇. (: The dynamic viscosity is -10 200848503 15 mm2 / sec ~ 30 mm2 / sec of the base oil with a given urea-based thickener 3 weight 7. More than 9 weight% is not full, even a small amount of lubricating oil It is still possible to ensure the load-bearing property of the rolling bearing in which the lubricating oil is sealed, and it is excellent in the ability to supply oil to the raceway surface under high-speed rotation. In particular, the monoamine component of the urea-based thickener is contained with respect to the entire monoamine. At least one monoamine' thickener selected from the group consisting of an aliphatic monoamine and an alicyclic monoamine is not easily broken by shearing force at a high speed, and is stabilized by a capillary phenomenon of a thickener. In the high-speed rolling bearing of the present invention, the lubricating oil is sealed inside, and in a state where the load is high in centrifugal force, the bearing does not flow out of the bearing, and the bearing can be stably supplied for a long period of time. The amount of oil required for lubrication, and the track surface of the high-speed sliding joint, can form an oil film of the required thickness for lubrication. Therefore, the bearing endurance life under high-speed rotation can be prolonged. Due to the raceway surface of the inner ring of the bearing, the outer ring Raceway surface At least one of the surface and the surface of the rotating body forms a plurality of dimples of the micro concave portion, which can improve the oil film forming ability of the contact surface of the orbital ring and the rotating body, and can obviously improve the lubricating oil life under the condition of the trace oil supply. The effect of the elongation is improved by forming at least one of the outer diameter surface selected from the inner ring of the bearing, the inner diameter surface of the outer ring of the bearing, and the surface of the rotating body by metal plating treatment or phosphoric acid coating treatment. The lubricating ability of the contact surface in the state of supply of a small amount of oil can significantly improve the prolongation of the life of the lubricating oil in the state of supply of a small amount of oil. Even if it is removed from the raceway portion and accumulated in the periphery, it is difficult to carry out the lubricating oil -11 - 200848503 In the case of the oil supply, the effect of the film is utilized, the diffusion of the base oil is facilitated, and the wettability is improved, thereby prolonging the life of the lubricating oil (burning bite). Since the inner surface of the pocket portion of the retainer has a concave portion, it is held in the concave portion. The lubricating oil is also supplied to the contact portion between the rotating body and the inner surface of the bag hole portion during the operation of the bearing, so that the lubrication state of the contact portion can be maintained well. Further, since at least the edge portion of the concave portion is chamfered, the lubricating oil adhering to the surface of the rotating body is not easily scraped off by the edge portion, and the lubricating oil is easily obtained at a necessary portion of the bag hole portion. As a result, it can be greatly extended at a high speed. The bearing endurance life of the bearing is such that at least a part of the inner surface of the bearing that is in contact with the lubricating oil forms a water-repellent oil-repellent film', even in a state of high centrifugal force, the oil of the lubricating oil can be moved to the raceway surface, Lubricating oil does not flow out of the bearing, and can stably supply the amount of oil required for bearing lubrication for a long period of time, and can form an oil film of lubricating thickness for the high-speed sliding contact track surface. Therefore, the bearing durability under high-speed rotation can be prolonged. [Embodiment] The rolling bearing for a speed of the present invention is not particularly limited in structure, and is, for example, a bevel ball bearing shown in Fig. 1. Fig. 1 is a longitudinal sectional view of a bevel ball bearing in which lubricating oil is sealed. The bevel ball bearing 1 is a bearing space formed by holding the rotating body 4 between the inner ring 2 and the outer ring 3 by the retainer 5 as shown in Fig. 1, and is fixed to the locking groove (provided outside) The sealing member 6 of the inner circumferential surface of the ring 3 is sealed to form a bevel ball bearing. At least the lubricating oil is sealed around the rotor 4 to form a lubricating oil bag hole 7 having a circumferential groove shape on the inner diameter surface of the outer ring 3 to physically prevent leakage of lubricating oil. A straight line connected by the contact points of the rotor 4 and the inner ring 2 and the outer ring 3 has a contact angle with respect to the radial direction, which can load the radial load and the axial load in one direction. The rotor 4 may be made of ceramic such as tantalum nitride or tantalum carbide. In the present invention, the bearing space formed by the inner ring 2, the outer ring 3 and the rotor 4 is sealed with the lubricating oil 8 for a high-speed bearing of the present invention to be described later. In another embodiment of the high-speed rolling bearing according to the present invention, at least one of the surface of the raceway surface selected from the inner ring of Fig. 1, the surface of the raceway surface of the outer ring, and the surface of the rotor is subjected to pit processing. Angular ball bearings. By the pit processing, pits of minute recesses are formed on the respective surfaces. The known method can be used as long as it is a method of forming a pit on the raceway surface of the orbital ring (inner ring and outer ring) of the bearing steel or the surface of the rotor. Specifically, bead blasting, cylinder honing, laser irradiation, etching, mold transfer, and the like can be employed. Among them, the use of the beading method is preferred from the viewpoint of cost and convenience. In the present invention, in order to form a pit on the raceway surface of the orbital ring and the surface of the rotor by the bead hit, for example, the bead material having a particle diameter of 30 to 300 00 m is directed toward the raceway surface of the orbital ring. The surface is 〇. 〇〗 ~! The pressure of MPa is sprayed for 1 to 60 seconds, thereby forming pits. As the bead material, any groove may be formed in the orbital ring or the rotating body formed of the bearing steel. Specifically, alumina, strontium carbide, glass beads, and the like are exemplified, and among them, alumina which is excellent in economical efficiency and workability is preferably used. -13- 200848503 The pit formed on the raceway surface of the orbital ring and the surface of the rotor by the above-mentioned pit processing, the depth from the surface of the raceway surface and the surface of the rotor should be 0·1~10/im, More preferably 1~5#m. When it is not reached, the effect of the pit becomes small and it is not good. If it is above 5 #m, the noise of the bearing becomes large, which is not good. The pits formed on the surface of the raceway surface of the orbital ring and the surface of the rotor are stable in order to stabilize the thickness of the oil film, and it is preferable to form pits periodically. Preferably, the dimple extends in a direction orthogonal to the rolling sliding direction. Thereby, the lubricating oil which is removed from the race portion and accumulated in the periphery can supply the oil more smoothly. According to another embodiment of the high-speed rolling bearing of the present invention, at least one of the outer diameter surface 2a of the inner ring 2 of the first drawing, the inner diameter surface 3a of the outer ring 3, and the surface of the rotor 4 is formed into a film. Beveled ball bearings. These films can be formed by performing a predetermined surface treatment on each side. The surface treatment is preferably one which reduces rotational friction and is not easily peeled off. In the surface treatment which is excellent in lubricity and is not easily peeled off, metal ore treatment or phosphoric acid film treatment is preferred. As the metal plating treatment, a method such as electroplating or electroless plating can be used. The metal to be used is preferably a soft material such as C u, A g , N i , Z η or S η and which is excellent in adhesion to a base material (bearing steel). The phosphoric acid film is treated, for example, by immersing an orbital ring or the like in a phosphate triester solution to form a metal phosphate film on the surface thereof. The phosphoric acid triester 'is an organic phosphoric acid compound represented by (R〇)3P = 0 (wherein R represents an aryl group, an aliphatic hydrocarbon group or an alicyclic hydrocarbon group), and can be used as a commercially available industrial material-14-200848503. Agents, etc. The phosphoric acid triester includes, for example, tricresyl phosphate (CH3C6H40)3P0, triphenyl phosphate (C6H5〇) 3p〇, tributyl phosphate (C4H9〇) 3PO, and the like. The above-mentioned phosphate triester may be diluted with an organic solvent and used as necessary in terms of handling. When the phosphate triester and the bearing steel are reacted to form a metal salt film on the surface thereof, the reaction speed may be increased while heating, for example, if it is immersed for about 1 to 2 hours at TC, it may be formed to have a sufficient thickness. In the lubricating oil to be described later, a phosphoric acid triester is mixed in advance, and a temperature of the bearing is increased, whereby a metal phosphate film can be formed on the contact surface between the rotor and the inner and outer rings. In another embodiment of the high-speed rolling bearing of the present invention, for example, the rotor body is held by the pocket portion of the retainer, and the inner surface of the pocket portion has a concave portion, at least the concave portion. The edge portion is chamfered to form the bevel ball bearing. Fig. 2 is a longitudinal sectional view showing the bevel ball bearing. Fig. 3 is a machined type retainer 1 used for the bevel ball bearing 1 A perspective view of 5. The bevel ball bearing 1 1, as shown in Fig. 2, holds the bearing space formed by the rotor 1 4 between the inner ring i 2 and the outer ring 13 by the retainer 15 Fixed to card The bevel ball bearing formed by the sealing member 16 (the inner circumferential surface of the outer ring 13) is sealed. The bearing space formed by the inner ring 12 and the outer ring! 3 and the rotating body 14 is sealed. The lubricating oil for high-speed bearing of the present invention will be described later. The straight line connected by the contact points of the rotor 14 and the inner ring 12 and the outer ring 13 has a contact angle with respect to the radial direction, which can be negative -15-. 200848503 Load-bearing load and shaft load in one direction. The rotor 1 4 can be made of ceramic such as tantalum nitride or tantalum carbide. As shown in Fig. 3, the inner surface of the pocket portion of the machined retainer 15 is disposed at 15a. The concave oil reservoir portion 15c and the relief portion 15b. Further, the edge portion 15d of the recess portion formed by the recess portions is subjected to chamfering processing. The oil reservoir portion 15c and the relief portion 15 b, only one of them may be provided. In addition to the edge of the recess, it is also possible to perform chamfering on all edges of the holder that may come into contact with the rotating body. In the same embodiment, for example, a bag using a holder The hole portion holds the rotating body, and has a concave portion on the inner surface of the bag hole portion, at least the edge portion of the concave portion is chamfered The deep groove ball bearing is constructed by this. Fig. 4 is a longitudinal sectional view showing the deep groove ball bearing in which the lubricating oil is sealed. Fig. 5 is a perspective view of the crown type retainer 25 used for the deep groove ball bearing. The deep groove ball bearing 2 1, as shown in Fig. 4, holds the bearing space formed by the rotor 24 between the inner ring 2 2 and the outer ring 23 by the retainer 25, and is fixed to the locking groove (provided in The deep groove ball bearing is formed by sealing the sealing member 26 of the inner circumferential surface of the outer ring 23, and the bearing space formed by the inner ring 2 2 and the outer ring 23 and the rotating body 24 is sealed with the high speed bearing of the present invention to be described later. The lubricating oil 27 can be made of a ceramic such as tantalum nitride or tantalum carbide. As shown in Fig. 5, a concave cross-sectional side storage is provided on the inner surface 2 5 a of the pocket portion of the retainer 25 . The oil portion 2 5 b and the bottom surface side oil reservoir portion 25 c are subjected to chamfering processing on the edge portion 2 5 d of the recess portion which is generated by the δ. In addition to the edge of the recess, it is also possible to carry out the chamfering process at all edges of the holder which may be in contact with the rotating body -16-200848503. The retainer assembled in the high speed rolling bearing of the present invention is preferably made of a resin. The resin retainer can reduce the weight of the bearing and reduce the influence of the centrifugal force under high-speed rotation. Further, it is possible to suppress frictional heat generation of the sliding portions of the rotating body and the retainer. As the resin holder, a resin having heat resistance and oil resistance should be used. For example, PA resin, polyethylene resin, polyacetal resin, polyethylene terephthalate resin, polybutylene terephthalate resin, polycarbonate resin, polyphenylene sulfide resin, polyether can be used. Anthracene resin, phenol resin, polyether oxime imide resin, polyamidoximine resin, PEEK resin, thermoplastic polyimide resin, and the like. These can be used singly or in combination of two or more. Among them, based on the viewpoints of light weight, excellent affinity with oil, and excellent mechanical stability, it is preferably PA resin reinforced with glass fiber or the like such as PA46 resin, PA66 resin or PA9T resin, or bakelite. (Bakelite) and other phenolic trees, the PEEK tree. In another embodiment of the high-speed rolling bearing according to the present invention, for example, as shown in Figs. 6 to 9, a bevel ball bearing in which a water-repellent oil-repellent film is formed on at least a part of the inner surface of the bearing which is in contact with the sealed lubricating oil is formed. In the high-speed rolling bearing which can sufficiently satisfy the high-speed rotation and the reduction of the working machine and the reduction in the operating cost, the high-speed rolling bearing can be used for the high-speed rolling bearing. At least a part of the inner surface of the bearing is provided with a water-repellent oil-repellent film, and a predetermined lubricating oil is sealed, and a rolling bearing having a long life of -17-200848503 at a high speed can be obtained. At least a part of the inner surface of the bearing that is in contact with the lubricant (the lubricating oil sealed in the bearing, etc.) forms a water-repellent oil-repellent film, and the surface tension of the water-repellent oil-repellent film prevents the lubricant from remaining on the surface of the film and moves it actively. . Therefore, the active lubricant moves continuously to the sliding surface such as the rotating surface and the raceway surface, and the lubrication can be improved to obtain a long-life rolling bearing. Fig. 6 is a cross-sectional view showing an example of a position at which the water-repellent oil-repellent film of the bevel ball bearing is formed. The water-repellent oil-repellent film may be formed on at least a part of the inner surface of the bearing which is in contact with the lubricating oil 37, and is preferably formed outside the sliding surface. The sliding surface herein includes an inner ring raceway surface 32a, an outer ring raceway surface 3 3 a, a contact surface of the retainer 35 and the rotor 34, a surface of the rotor 34, and the like. The bevel ball bearing 3 1 of Fig. 6 holds the bearing space formed by the rotating body 34 between the inner ring 3 2 and the outer ring 3 3 by the retainer 35, and is fixed to the locking groove (g The sealing member 36 of the inner circumferential surface of the outer ring 33 is sealed 'and a water-repellent oil-repellent coating 38 8 a is formed on a part of the inner side surface of the bearing of the sealing member 36. The bearing space formed by the inner ring 3 2 and the outer ring 3 3 and the rotor 34 is sealed with the lubricating oil for high-speed bearing 37 of the present invention to be described later. A straight line connected by the contact points of the rotating body 34 and the inner ring 3 2 and the outer ring 33 has a contact angle /3 with respect to the radial direction, which can load the radial load and the axial load in one direction. Further, the rotating body 34 can be made of ceramics such as tantalum nitride or tantalum carbide. Fig. 7 to Fig. 9 are cross-sectional views of other examples of the formation position of the above-mentioned water-repellent oil-repellent film -18-200848503. Fig. 7 is a view showing an inner diameter surface other than the raceway surface 3 3 a of the outer ring, and a water-repellent oil-repellent coating 38b on the inner side surface of the bearing of the sealing member 36; Fig. 8 is a track-removing surface of the inner ring An outer diameter surface other than 32a and a bearing inner side surface of the sealing member 36 form a water-repellent oil-repellent coating 3 8 c; and a ninth drawing is formed on the surface of the retainer 35 other than the contact surface with the rotating body 34 Water dialing oily film 3 8d. The structures other than the water-repellent oil-repellent film in Fig. 7 to Fig. 9 are the same as those in Fig. 6. In the sixth to ninth drawings, the positions at which the water-repellent oil-repellent coating film is formed are individually displayed, but these forming positions may be used singly or in combination of two or more. Further, in the same embodiment, for example, Figs. 10 to 13 show that a deep groove ball bearing of a water-repellent oil-repellent film is formed on at least a part of the inner surface of the bearing which is in contact with the sealed lubricating oil. The first drawing shows a cross-sectional view showing an example of the position of the water-repellent oil-repellent film of the deep groove ball bearing. The water-repellent oil-repellent film may be formed on at least a part of the inner surface of the bearing that is in contact with the lubricating oil 47, and is preferably formed outside the sliding surface. The sliding surface herein includes an inner ring raceway surface 42a, an outer ring raceway surface 43a, a contact surface of the retainer 45 with the rotor 44, a surface of the rotor 44, and the like. The deep groove ball bearing 41 of Fig. 10 is a bearing space formed by holding the rotating body 44 between the inner ring 42 and the outer ring 43 by the retainer 45, and is fixed to the locking groove (provided in the outer ring 4). The sealing member 46 of the inner peripheral surface of 3 is sealed 'and a water-repellent oil-repellent coating 48 8 a is formed in a part of the inner side surface of the bearing of the sealing member 46. In the bearing space formed by the inner ring 4 2 and the outer ring 43 and the rotating body 4 4 - 47 ° 200848503, the lubricating oil for the high-speed bearing of the present invention and the rotating body 44 may be made of tantalum nitride, tantalum carbide, or the like. Made of ceramic. Figs. 1 to 1 are cross-sectional views showing other examples of the formation of the water-repellent oil-repellent film. In the first aspect, the oil-repellent coating 48b is formed on the inner diameter surface of the outer ring except the raceway surface, and the inner surface of the bearing of the seal member 46; and Fig. 12 is the outer diameter of the inner raceway surface 42a. The inner surface of the bearing surface of the sealing member 46 forms a water-repellent coating 48c. Fig. 13 shows a water-repellent oil-repellent coating 48 d formed on the surface of the retainer 45 except for contact with the rotor 44. No.: Fig. 13 is the same as the structure other than the water-repellent oil-repellent film. Although Fig. 10 to Fig. 1 3 show the position of the water-repellent coating film individually, these forming positions may be used alone or in combination of two or more. By forming the water-repellent oil-repellent coatings 38a to 38d and 48a to 48d on the inner surface of the bearing as shown in Fig. 1 to Fig. 3, the surface tension of the water-repellent coatings 38a to 38d, 48a to 48d can be avoided. The sealed lubricating oils 37 and 47 are left on the surface of the film to be movable, for example, on the raceway faces 32a and 42a and the outer ring raceway faces 33a and 43a where the films 38a to 38d, 48a to 48d are not formed. The contact faces of the retainers 3ί with the rotors 34, 44, the surfaces of the rotors 34, 44, and the like are continuously supplied with the lubricating oils 37, 47, thereby enhancing the holding of the lubricating action and becoming a long-life rolling bearing. Further, by forming a water-repellent film position 43a outside the sliding surface, the oil-repellent surface is made of a water-repellent surface in the form of a figure of 1 and a sixth oily property. Due to inner ring, 45, etc., continuity, -20-200848503 Avoid the peeling of the film caused by sliding. The material used for forming the water-repellent oil-repellent film may be a water-repellent oil-repellent agent, and is not particularly limited. The water-repellent coating is preferably a water-repellent oil-repellent film formed of a fluoroalkyl decane composed of a hydrazine-based water-repellent agent such as decane-oxygen. The commercially available product includes, for example, a product of Mektron: Nokusgard ST-420, Dajindyne, manufactured by Shin-Etsu Chemical Co., Ltd.: perfluoroalkyl decane KBM7803, the above-described embodiment of the high-speed rolling bearing of the present invention The method of forming the water-repellent oil-repellent film on the inner surface of the bearing in contact with the lubricating oil is not particularly limited. In order to form a water-repellent oil-repellent film on the inner surface of the bearing, it is possible to form a water-repellent oil-repellent film in a dispersion of a sand-based water-repellent oil-repellent agent such as sand courtyard oxygen. It can also be used: vacuum steaming (PVD), chemical vapor deposition (CVD), ion plating, etc., etc. It is also possible to use a commercially available water- and water-repellent agent to be applied to the inner surface of the bearing to form a water-repellent oil-repellent film. Among them, each part is separately treated with water and oil, and the processing cost is better. The rolling bearing is immersed in the water-repellent and oil-repellent: method. In the high-speed rolling bearing of the present invention, it is preferable that the lubricating oil product % of the enclosed volume is 1% by volume or more and 1% by volume or less, and the amount of lubricating oil required for lubrication is insufficient, and the right-handed sand-based or fluorine-repellent coating is more likely to occur. Membrane, or use the United States can be multi-functional industrial system: Unisys and so on. State, as long as it is in contact with the chemical film, contact with the lubricating oil to dip the rolling bearing, dry and shape I, physical vapor deposition dry plating, or contact with lubricating oil, based on the point of view that does not need to be profitable, in the sweat The square bearing volume of the part. If it does not reach 1 body and exhaustion. If it is 1 〇 -21 - 200848503 vol% or more, the mixing torque becomes large and the heat becomes large, which not only does not extend the lubrication life, but also increases the cost and is not good for the environment. In addition to the bevel ball bearing and the deep groove ball bearing shown in each of the above embodiments, the high speed rolling bearing of the present invention can also be used with a cylindrical roller bearing, a tapered roller bearing, a self-aligning roller bearing, and a needle roller. Bearings, thrust cylindrical roller bearings, thrust tapered roller bearings, thrust pin roller bearings, thrust self-aligning roller bearings, etc. Among them, it is preferable to use a bevel ball bearing or a cylindrical roller bearing based on the viewpoint of both the rotation accuracy and the load-bearing performance of the high-speed rotation. The high-speed rolling bearing according to the present invention is characterized in that a high-speed bearing lubricating oil comprising the following base oil and a urea-based thickener is used. As the base oil of the present invention, a lubricating oil having a dynamic viscosity at 40 ° C (hereinafter referred to as dynamic viscosity) of 15 to 30 mm 2 /Sec can be used. It is preferably a lubricating oil having a dynamic viscosity of 15 to 25 mm 2 /sec. In the case where the dynamic viscosity is less than 15 mm 2 /sec, the viscosity is too low to obtain sufficient load resistance. Also, in the case where the dynamic viscosity exceeds 30 mm 2 /se C, the amount of oil supplied to the raceway surface under high-speed rotation is insufficient, and the bearing life is terminated early. The type of the above lubricating oil is preferably a synthetic hydrocarbon oil, an ester oil, an alkyl diphenyl ether oil, or a mixed oil of these. Further preferably, the dynamic viscosity of each of the synthetic hydrocarbon oil, the ester oil, and the alkyl diphenyl ether oil is from 15 to 30 mm 2 /sec. If it is in this range, even in the case of being a mixed oil, the dynamic viscosity can be ensured to be in the range of 1 5 to 3 0 m 2 / s e c . In the case of a mixed oil, a mixed oil of a synthetic hydrocarbon oil and an ester oil is preferred. The mixing ratio is preferably such that the synthetic hydrocarbon oil/ester oil (weight ratio) = 8/2 to • 22 - 200848503 2/8. More preferably, the weight ratio of the synthetic hydrocarbon oil is more than the same amount of the ester oil. Further, an alkyl diphenyl ether oil can also be used alone. As the synthetic hydrocarbon oil, for example, a poly-α-olefin such as a paraffin wax, an isostone, an alkene, a polyisobutylene, a 1-decene oligomer, a total oligomer of a terpene and ethylene, or the like is included. In the case of ester oils, for example, dibutyl sebacate, di-2-hexyl sebacate, dioctyl adipate, diisodecyl adipate, tridecyl adipate a diester oil of ester, ditridecyl ester, methyl ethyl hydrazide dioxime; aroma of trioctyl trimellitate, tridecyl trimellitate octyl trimellitate Alkyl ester oil; a polyol ester oil such as trimethylolpropane ester, trimethylolpropane decanoate, pentaerythritol-2-ethylhexanoate or tetraol phthalate, a carbonate oil or the like. The alkyl diphenyl ether oil includes, for example, a monoalkyldiphenyl ether alkyl diphenyl ether, a polyalkyl diphenyl ether, and the like. The base oil used in the lubricating oil for high-speed bearing of the present invention has a surface of 25 mN/m or more, preferably 27 to 40 mN/m, and a density of g/cm3 or less, preferably 0. 8~0. 93 g/cm3. If the surface tension is not: mN/m, it is not easy to use the capillary phenomenon to move to the raceway portion, and the amount of oil required for the high-speed supply is not required. If the density exceeds 0. 95 g/cm3, it is not easy to use the capillary phenomenon to move to the raceway portion, and it is impossible to stabilize the amount of oil required at high speed. The urea-based thickener used in the lubricating oil for high-speed bearings of the present invention is obtained by reacting a polyisocyanate component with a monoamine component. The polyisocyanate component includes, for example, a p-phenylene dimer polybutide ethyl, a diester, etc., a tetraoctanoic acid pentamer. 95 t 25 is also supplied as stable, cyanate-23-200848503 ester, toluene diisocyanate, diphenyl diisocyanate, diphenylmethane diisocyanate, octadecyl diisocyanate, decyl diisocyanate, hexane diisocyanate Xiao Wei and so on. Among them, aromatic diisocyanate is preferred. Further, the polyisocyanate obtained by reacting a diamine and a molar excess of diisocyanate can also be used. The diamine may, for example, be ethylenediamine, propylenediamine, butylamine, hexamethyleneamine, octanediamine, phenylenediamine, toluenediamine, xylenediamine, diaminodiphenylmethane or the like. The monoamine component contains 50 mol% or more, preferably 80 mol% or more, of at least one monoamine selected from the group consisting of an aliphatic monoamine and an alicyclic monoamine. By containing 50 moles /. As described above, the thickener is not easily broken by the shearing force at a high speed, and the capillary phenomenon of the thickener fiber can stably supply the oil in the lubricant to the raceway surface. The monoamine other than the aliphatic monoamine and the alicyclic monoamine is, for example, an aromatic monoamine. As the aliphatic monoamine, there may be mentioned hexylamine, octylamine, dodecylamine, hexadecylamine, stearylamine, stearylamine, oleylamine and the like, among which decamethylamine is preferred. In the case of an alicyclic monoamine, for example, cyclohexylamine or the like. As the aromatic amine, aniline, p-toluidine or the like can be cited, and among them, p-toluidine is preferred. The urea-based thickener of the present invention has a content of 3 parts by weight based on the entire lubricating oil. /. The above 9% by weight is less than, preferably 5% by weight to 9% by weight. When the blending amount is less than 3% by weight, the 'base oil retaining ability is insufficient', especially in the initial stage of rotation, a large amount of oil is temporarily separated and the lubricating oil leaks -24-200848503, which results in a shortened bearing durability life. Further, if the blending amount exceeds 9% by weight, the relative content of the base oil becomes small, and the oil supply property is deteriorated, and the insufficient lubrication is caused earlier, and the bearing durability life is shortened in the same manner. Further, in the lubricating oil for high-speed bearing of the present invention, a known additive for lubricating oil may be contained as needed. The additive includes, for example, an oxidation preventive agent such as an organic zinc compound, an amine system or a phenol compound; a metal deactivator such as benzotriazole; and a viscosity index enhancer such as polymethacrylate or polystyrene; a solid lubricant such as molybdenum disulfide or graphite; a rust preventive agent such as a metal sulfonate or a polyhydric alcohol ester; a friction reducing agent such as an organic molybdenum; an oily agent such as an ester or an alcohol; and a wear preventing agent such as a phosphorus compound; Wait. These can be added singly or in combination of two or more. The content of the additive is preferably 个别. 〇 5% by weight or more, the total amount of the lubricating oil is 0. 1 5 to 1 0% by weight range. When the total amount is more than 10% by weight, the effect of increasing the content is not expected, and the relative content of other components is reduced, and aggregation of the additive may occur in the lubricating oil, which may cause an undesirable phenomenon such as an increase in torque. In recent years, in the general-purpose motor such as an AC motor or a DC motor, the bearing tends to rotate at a higher speed and a higher surface pressure as the motor is miniaturized. In the conventional method of using a metal soap lubricating oil such as lithium soap, it is not possible to obtain sufficient durability, and there is a tendency to use a urea-based lubricating oil which is more excellent in durability. The motor used for electrical auxiliary equipment directly related to the automobile engine is used at a temperature of 150 ° C or higher; a motor for a ventilating fan, a blower motor for a fuel cell, an air cleaner motor, a fan motor, a servo motor, a stepping motor The motor used for industrial machinery or information equipment, etc., the operating temperature of the motor of the electric machine such as the starter motor, the electric steering wheel motor, the pitch control motor, the wiper motor, and the electric window motor of the steam meter - 200848503 It is a lower temperature of less than 150t. In such a low-temperature use environment, the fluidity of the base oil of the conventional urea-based lubricating oil is not good, and in the case where higher speed is required, the base oil supplied to the raceway surface is insufficient, and there is a tendency to be lubricated. Bad problem. The high-speed rolling bearing in which the high-speed bearing lubricating oil of the present invention is enclosed has an excellent oil supply property of the raceway surface even in an environment requiring high speed at the above-mentioned lower temperature, even for the above-mentioned ventilating fan. Motor, fuel cell blower motor, air cleaner motor, fan motor, servo motor, stepper motor, etc. for industrial machinery or information machine motor's starter motor, electric steering wheel motor, direction adjustment pitch control motor, Motors for electric machines such as wiper motors and electric window motors can also be suitably used. EXAMPLES Hereinafter, the present invention will be further illustrated by Test Examples, but the present invention is not limited thereto. The data of the base oil density (15 ° C) and the dynamic viscosity (40 ° C) used in the respective examples and comparative examples are shown in Tables 1 to 5. The consistency shown in Table 1 to Table 5 is based on ns K2220 5. The 60 mixed consistency measured by 3; the surface tension of the base oil at 25 ° C is the measured enthalpy measured by a Du Nouy ring simple surface tension meter. The centrifugal oil separation shown in Tables 1 to 5 is the enthalpy measured by the centrifugal oil separation test used. -26- 200848503 &lt;Centrifugal oil separation test&gt; Using a centrifugal separator, 50 g of the lubricating oil sample was placed in a centrifugal separation tube, and centrifuged at 4 (TC, 2 3 000 G for 7 hours) to obtain a centrifugal oil according to the following formula. (centrifugal oil degree %) = (1 - increase in the concentration of the test agent per test / concentration of the thickener after the test) X 1 0 0 Example 1 to Example 5, Comparative Example 1, Comparative Example 2 And Comparative Example 5 In the half amount of the base oil shown in Table 1, 4,4'-diphenylmethane diisocyanate was dissolved in the ratio shown in Table 1 (manufactured by Nippon Polyurethane Industry, Miriam T. , hereinafter referred to as M DI ), in the remaining half of the base oil, dissolved in the MD 12-fold equivalent of monoamine. The mixing ratio and type of each are as shown in Table 1. The solution dissolved in M DI is stirred and dissolved. After the solution of the monoamine is added, the mixture is continuously stirred at 100 to 120 ° C for 30 minutes to carry out a reaction, thereby producing a diurea compound in the base oil to obtain a lubricating oil sample. Base oil density, dynamic viscosity, surface used. The measurement results of the tension are shown in Table 1. The consistency of the obtained lubricating oil sample and the centrifugal oil separation were measured. High speed tests at room temperature as shown in the lubricating oil, the oil life at high speed between the measured ambient temperature. The measurement results in Table 1 finishing. &lt;Normal temperature high-speed lubricating oil test-Deep groove ball bearing (6204) &gt; The lubricating oil sample 0.14 g (about 3% by volume of the bearing full space volume) is aligned with the raceway surface and sealed into the deep groove ball bearing (6204) , the implementation of non-contact -27- 200848503 touch seal to make each test bearing. The test bearing load was loaded with an axle load of 6 70 N and a radial load of 67 N, and rotated at a rotational speed of 15,000 rpm under a normal temperature environment, and the time until the occurrence of the burnt bit was measured as the life of the lubricating oil. In this endurance test, the product of the pitch diameter dm (mm) of the bearing and the number of revolutions N (rpm) (dmN値) was 520,000. Comparative Example 3 and Comparative Example 4 A lubricating oil sample was prepared by blending a base oil and lithium stearate in the proportions shown in Table 1. The same items as in Example 1 were measured for the base oil and lubricating oil samples used. The results are summarized in Table 1. &lt;Normal temperature high speed ball bearing test - beveled ball bearing&gt; The lubricating oil sample of Example 1, Example 2, Example 5, Comparative Example 1 to Comparative Example 3 or Comparative Example 5 was 3.0 g (about the entire volume of the bearing) 10% by volume) is aligned with the raceway surface and sealed with beveled ball bearings (outer diameter 150 mm X inner diameter 100 mm, inner and outer rings SUJ2, rotating body 13/32 turns of tantalum nitride balls), non-contact sealing And made each test bearing. Under the constant pressure of the test bearing with a pressure of 1 · 8 GPa, the bearing is cooled by the cooling of the outer cylinder to keep the outer ring of the bearing below 50 ° C, and rotate at a rotational speed of 1 4 00 rpm. The time until burnt bite occurred was measured as the life time of the lubricating oil. In the endurance test, the product of the pitch diameter dm (mm) of the bearing and the number of revolutions N (rpm) (dmN値) was 18.5 million. -28- 200848503 [Table 1] Example: 匕1 column 1 2 3 4 5 1 2 3 4 5 Lubricating oil compounding (% by weight) Base oil synthetic hydrocarbon oil n - - - - - 94.9 - - - - Synthetic hydrocarbon Oil 2) 62 47.5 46.5 60 - - - 46 - 57 Ester oil 3) 33 47.4 46.5 32 One - - 46 - 31 Ester oil 4) 93 Alkyl diphenyl ether oil 5) - - - - 93 - - - - - Anthrone oil 6) 80 - Base oil density (g/cm3) 0.86 0.88 0.88 0.86 0.93 0.8 0.99 0.88 0.95 0.86 4〇°C base oil dynamic viscosity (_2/sec) 23 19 19 23 22 5 53 19 16 22 Base oil surface tension at 25 ° C (mN / m) 31.5 30.5 30.5 31.5 35.4 28.1 33.7 30.5 22.7 31.5 Thickener lithium stearate 8 20 Monoamine: octylamine 2.5 1.8 2.8 — 2.8 1.8 2.8 - - 6.1 Monoamine: Cyclohexylamine - 0.7 - 3.5 - 0.7 - mono-monoamine: p-toluidine - - 0.6 - 0.6 - 0.6 - - - diisocyanate: mdi7) 2.5 2.6 3.6 4.5 3.6 2.6 3.6 - - 5.9 (total of lubricating oil) 98 100 100 100 100 100 100 100 100 100 Consistency 300 290 290 270 290 320 280 290 280 260 Centrifugal oil separation % 28 24 18 16 20 33 12 38 41 7 Normal temperature high speed lubricant life h 6204 bearing , dmN = 520,000 &gt; 1500 &gt; 1500 &gt; 1500 1250 &gt; 1500 270 320 110 40 640_ Bevel ball bearing, dmN = 1.85 million &gt; 1000 &gt; 1000 - - &gt; 1000 190 260 50 - 320_ 1) Density 0.80 g/cm3 '40°C dynamic viscosity 5 _2/sec, Nippon Steel Chemical Co., Ltd., Xinfuluote 2012) f degree 0.83 g/cm3, 40°C dynamic viscosity 30 mm2/SeC, Nippon Steel Chemical Co., Ltd. , Xinfuluote 601 3) f degree 0.92 g/cm3, 40 °C dynamic viscosity 12 mm2/SeC, Ciba special chemical system, Leoup DOS4) density 0.99 g/cm3 ' 4 (rc dynamic viscosity 53 Mm2/sec, Ciba Specialty Chemicals, Leopold LPE602 5) Density 0.93 g/cm3, 4 〇. (: dynamic viscosity 22 mm2 / Sec, made by Matsumura Petroleum Research Institute, Moresko Hajupup LB226) density 0.95 g / cm3, 4 (TC dynamic viscosity 16 mm2 / Sec, Toray Dow Corning, SH200 (20 7) Made in Japan Polyurethane Industry, Miriam Neve] ^ Ding-29- 200848503 As shown in Table 1, the lubricating oil used in the present invention is preferably: (1) The dynamic viscosity at 40 C is 15 mm 2 /sec~ The base oil of 30 mm 2 /sec contains 3% by weight or more and 9% by weight of the urea-based thickener which is less than full; (2) the monoamine component of the urea-based thickener contains 5 Torr of the total amount of the monoamine. % or more of a monoamine component selected from at least one monoamine of an aliphatic monoamine and an alicyclic monoamine; (3) a base oil having a surface tension of 25 mN/m or more and a density of 0.95 g/cm 3 or less; The base oil is a mixed oil of a hydrocarbon oil, an ester oil, an alkyl diphenyl ether oil or the like. Example 6 to Example 9 and Comparative Example 8 In the half amount of the base oil shown in Table 2, MDI was dissolved in the ratio shown in Table 2, and in the remaining half of the base oil, 2 times equivalent of MDI was dissolved. Monoamine. The matching ratios and types of each are shown in Table 2. While stirring the solution dissolved in the MDI, the solution in which the monoamine was dissolved was added, and the mixture was continuously stirred at 100 ° C to 120 ° C for 30 minutes to carry out a reaction, whereby a diurea compound was formed in the base oil. A lubricant sample was prepared. The results of measurement of the base oil density, dynamic viscosity, and surface tension used are shown in Table 2. The consistency and centrifugal oil separation of the obtained lubricating oil sample were measured. Further, the normal temperature high-speed lubricating oil test shown below was carried out to measure the normal-temperature high-speed lubricating oil life time. The measurement results are summarized in Table 2. &lt;Normal temperature high-speed lubricating oil test-Deep groove ball bearing (6204) &gt; Alumina sprayed with a particle size of #1〇〇 (particle size 106~i49//m) at a pressure of 0.2 MPa by a bead shot method Secondly, the outer ring track surface of the deep groove ball bearing -30- 200848503 (62 04 ) is subjected to a pit process of 2 to 3 μm deep on the outer ring track surface, thus forming a test bearing. The lubricating oil sample 〇 3 2 3 5 g (about 5% of the total volume of the bearing) is placed on the raceway surface to seal the test bearing, and the non-contact seal is applied to form each test bearing. The test bearing load was loaded with a load of 607 N and a load of 6 7 N, and was rotated at a rotation speed of 100 rpm under a normal temperature environment, and the time until the occurrence of the burnt bit was measured as the life time of the lubricant. In this endurance test, the product of the pitch diameter dm (mm) of the bearing and the number of revolutions N (rpm) (dmN値) was 350,000. Comparative Example 6 to Comparative Example 7 A lubricating oil sample was prepared by blending a base oil and lithium stearate in the ratios shown in Table 2. The same items as in Example 6 were measured for the base oil and lubricating oil samples used. The results are summarized in Table 2. &lt;Normal temperature high-speed lubricating oil test-oblique-angle ball bearing&gt; By the bead blasting method, the oxidized bromine of particle size #100 (particle size 106~149&quot; m) is sprayed at a pressure of 0.2 MPa for about 20 seconds on the bevel ball bearing The outer ring raceway surface (outer diameter 150 mm x inner diameter 100 mm, inner and outer ring SUJ2 'rotating body 13/32 turns of tantalum nitride ball) is subjected to pit processing of 2 to 3 A m deep on the outer ring raceway surface. This was made into a test bearing. 3.0 g of the lubricating oil samples of Examples 6 to 9 and Comparative Examples 6 to 8 (about 10% by volume of the entire bearing volume) were aligned with the raceway surface, and the test bearing was sealed, and each of the test bearings was formed by non-contact sealing. . In the test bearing, the outer ring of -31 - 200848503 1 . 8 G P a is kept rotating. Measure the endurance test 1 (rpm), 2 〇 B B 卩 下 ' 'cool the bearing by cooling the outer cylinder so that the shaft is below 50C, and the bite occurs at the rotation speed of the M5 〇 () claw The time until the life of the lubricating oil is 0. The pitch diameter dm (mm) of the bearing and the number of revolutions N (dmN値) of the bearing are 1.85 million. The measurement results are summarized in Table-32-200848503 [Table 2] Comparative Example 6 7 8 9 6 7 8 Lubricating oil blending (% by weight) Base oil synthetic hydrocarbon oil]) 62.5 46.5 60 46 46 57 Ester oil 2) 33 46.5 A 32 46 46 31 Alkyl diphenyl ether oil 3) — - 93 - - - - Base oil density (g/cm3) 0.86 0.88 0.93 0.86 0.88 0.88 0.86 40 °C base oil dynamic viscosity (mm2/sec) 23 19 22 23 19 19 22 25t: base oil surface tension (mN / m) 31.5 30.5 35.4 31.5 30.5 30.5 31.5 Thickener lithium stearate 8 8 Monoamine: octylamine 2.5 2.8 2.8 - - - 6.1 Monoamine: Cyclohexylamine - 3.5 A - - Monoamine: p-toluidine — 0.6 0.6 - - - - Diisocyanate: mdi4) 2.5 3.6 3.6 4.5 - — 5.9 (Total lubricating oil combination) 100 100 100 100 100 100 100 Consistency 300 290 290 270 290 290 260 Centrifugal oil separation% 28 18 20 16 38 38 7 There are some bead hits and j\\\ te jw\ normal temperature high speed lubricant life h 6204 bearing, dmN=350,000>2000 &gt;2000 &gt;2000 &gt ;2000 470 210 550 Bevel ball bearing, dmN=1.8 million - &gt;2000 - - 220 50 320 1) Density 0.83 g/cm3, 40°C dynamic viscosity 30 mm2/Sec, Nippon Steel Chemical System, Xinfu Road Special 601

2) 密度0.92 g/cm3，40°C動黏度12 mm2/sec，汽巴特殊化學品製，雷歐路普DOS 3 )密度0.93 g/cm3，40°C動黏度22 mm2/sec，松村石油硏究所製，摩列斯科哈依路 普 LB222) Density 0.92 g/cm3, 40°C dynamic viscosity 12 mm2/sec, Ciba Specialty Chemicals, Leopold DOS 3) Density 0.93 g/cm3, 40°C dynamic viscosity 22 mm2/sec, Songcun Petroleum Research Institute, Moresko Hayupup LB22

4)曰本聚氨酯工業製，密利歐聶特MT 從表2可知，本發明所使用的潤滑油較佳爲：（1 ) 在40°C的動黏度爲15 mm2/sec〜30 mm2/sec的基油中， 含有3重量％以上9重量％未滿之脲系增稠劑；（2 )脲系 -33- 200848503 增稠劑的單胺成分，是相對於單胺全體含有5 0莫耳％以上 的選自脂肪族單胺及脂環式單胺中至少1種單胺之單胺成 分；（3 )基油的表面張力爲 25 mN/m以上，且密度爲 0 · 9 5 g / c m3以下；基油係合成烴油、酯油、烷基二苯醚油 或其等的混合油。又（4 )進一步在選自軸承的內環的滾 道面表面、外環的滾道面表面、轉動體的表面中至少-個 實施凹坑加工則更佳。 實施例1 〇〜實施例1 3、比較例1 2及比較例1 3 在表3所示的基油的一半量中，依表3所示的比例溶 入MDI，在剩下一半的基油中，溶入MDI2倍當量的單 胺。各個的配合比例及種類如表3所示。 邊將溶入MDI的溶液攪拌，邊將溶入單胺的溶液加 入後，以100〜12 0 °C持續攪拌30分鐘以進行反應，藉此 在基油中生成二脲化合物而製得潤滑油試料。所使用的基 油密度、動黏度、表面張力的測定結果顯示於表3。測定 所製得的潤滑油試料之稠度及離心離油度。又進行以下所 示的常溫高速潤滑油試驗，測定常溫高速潤滑油壽命時 間。測定結果整理於表3。 比較例9〜比較例1 1 將基油和硬脂酸鋰以表3所示的比例配合而製得潤滑 油試料。對於所使用的基油和潤滑油試料，係測定和實施 例1 0同樣的項目。結果整理於表3。 -34 - 200848503 &lt;常溫高速潤滑油試驗-深槽滾珠軸承（6204 )〉 在實施例1 〇、實施例1 3及比較例9，使用氰化銅浴 (氰化亞銅、氰化鈉、氫氧化鉀，5 0〜6 0 °C )，對深槽滾 珠軸承（6204 )的內環外徑、外環內徑實施金屬鍍敷處 理，如此作成試驗軸承。所形成的鍍膜厚度約20 // m。在 實施例1 1、實施例1 2及比較例1 〇，係將磷酸三甲苯酯 7.36g用2-丙醇稀釋而調製成200 ml的磷酸三甲苯酯溶 液，將深槽滾珠軸承（6204 )的內外環浸漬於該溶液中2 小時（溶液溫度60 °C )，藉此在表面形成磷酸金屬鹽被 膜，而作成試驗軸承。在比較例1 1〜比較例1 3，是用未 形成被膜的深槽滾珠軸承（6204 )作爲試驗軸承。 將表3所示的潤滑油試料0.023 5g (軸承全空間容積 的約0.5體積％ )對準滾道面而封入該試驗軸承，實施非 接觸密封而作成各個試驗軸承。讓試驗軸承負荷軸荷重 67 0N和徑荷重67N，在常溫環境下以10000 r pm的旋轉速 度旋轉，測定迄燒咬發生爲止的時間作爲潤滑油壽命時 間。該耐久試驗中，軸承的節圓直徑dm ( mm )和轉數N (rpm)的乘積（dmN値）爲34萬。 &lt;常溫高速潤滑油試驗-斜角滾珠軸承&gt; 在比較例9，是使用氰化銅浴（氰化亞銅、氰化鈉、 氫氧化鉀，50〜60 °C )，對斜角滾珠軸承（外徑150 mm X 內徑100 mm，內外環 SUJ2，轉動體13/32吋的氮化矽 -35- 200848503 球）的內環外徑、外環內徑實施金屬鍍敷處理，如此作成 試驗軸承。所形成的鍍膜厚度約2 0 # m。在實施例1 1及 比較例10，係將磷酸三甲苯酯7.3 6g用2-丙醇稀釋而調製 成200 ml的磷酸三甲苯酯溶液，將斜角滾珠軸承（和上 述相同）的內外環浸漬於該溶液中2小時（溶液溫度60 °C )，藉此在表面形成磷酸金屬鹽被膜，而作成試驗軸 承。在比較例1 1〜比較例1 3，是用未形成被膜的斜角滾 珠軸承（和上述相同）作爲試驗軸承。 將表3所示的潤滑油試料3.0g (軸承全容積的約1〇% 體積）對準滾道面而封入該等試驗軸承，實施非接觸密封 而作成各個試驗軸承。在對試驗軸承用1 · 8 GPa的定壓加 壓下，藉由外筒冷卻將軸承冷卻以使軸承外環保持在5 〇 t 以下，並以1 45 00 rpm的旋轉速度進行旋轉。測定迄燒咬 發生爲止的時間作爲潤滑油壽命時間。該耐久試驗中，軸 承的節圓直徑dm ( mm )和轉數N ( rpm )的乘積（dmN 値）爲185禹。 •36- 200848503 [表3] 實施例 比較例 10 11 12 13 9 10 11 12 13 潤滑油配合(重量％) 基油 合成烴油1] 62 46.5 60 46 46 46 57 46.5 酯油2) 33 46.5 - 32 46 46 46 31 46.5 院基二苯基醚油3) - - 93 - - - - 基油密度(g/cm3) 0.86 0.88 0.93 0.86 0.88 0.88 0.88 0.86 0.88 40°C的基油動黏度(mm2/Sec) 23 19 22 23 19 19 19 22 19 25°C的基油表面張力（mN/m) 31.5 30.5 35.4 31.5 30.5 30.5 30.5 31.5 30.5 增稠劑 硬脂酸鋰 8 8 8 單胺:辛胺 2.5 2.8 2.8 - - - - 6.1 2.8 單胺:環己胺 一 - — 3.5 - - - - - 單胺:對甲苯胺 - 0.6 0.6 0.6 二異氰酸酯:mdi4) 2.5 3.6 3.6 4.5 - - - 5.9 3.6 (潤滑油配合合計） 100 100 100 100 100 100 100 100 100 稠度 300 290 290 270 290 290 290 260 290 離心離油度％ 28 18 20 16 38 38 38 7 18 鑛銅處理 有 一 - 有 有 - - - - 磷酸被膜處理 - 有 有 一 - 有 - - - 常溫高速潤滑油壽命h 6204 軸承，dmN=34 萬 &gt;2000 &gt;2000 &gt;2000 &gt;2000 430 460 210 550 1530 斜角滾珠軸承，dmN=185萬 - &gt;2000 - - 140 180 50 320 260 1) 密度0·83 g/cm3，4(TC動黏度30 nW/sec，新日鐵化學製，新福路特6014) 曰 聚氨酯 聚氨酯 聚氨酯 聚氨酯 聚氨酯 聚氨酯 聚氨酯 聚氨酯 聚氨酯 聚氨酯 聚氨酯 从 从 从 从 聚氨酯 聚氨酯 聚氨酯 聚氨酯 聚氨酯 聚氨酯 聚氨酯 聚氨酯 聚氨酯 聚氨酯 聚氨酯 聚氨酯 MT MT 聚氨酯 MT 聚氨酯 聚氨酯 MT MT MT MT MT 聚氨酯 聚氨酯 聚氨酯 聚氨酯 聚氨酯 聚氨酯 聚氨酯 聚氨酯 聚氨酯 聚氨酯 聚氨酯 聚氨酯The base oil contains 3% by weight or more and 9% by weight of the urea-free thickener; (2) the monoamine component of the urea-33-200848503 thickener, which contains 50 moles relative to the entire monoamine. More than % of a monoamine component selected from at least one monoamine of an aliphatic monoamine and an alicyclic monoamine; (3) a base oil having a surface tension of 25 mN/m or more and a density of 0 · 9 5 g / C m3 or less; the base oil is a mixed oil of a synthetic hydrocarbon oil, an ester oil, an alkyl diphenyl ether oil or the like. Further, (4) it is more preferable to perform pit processing on at least one of the raceway surface selected from the inner ring of the bearing, the raceway surface of the outer ring, and the surface of the rotor. Example 1 〇~Example 1 3, Comparative Example 1 2 and Comparative Example 1 3 In half the amount of the base oil shown in Table 3, MDI was dissolved in the ratio shown in Table 3, and half of the base oil was left. Medium, a monoamine equivalent to twice the equivalent of MDI. The proportions and types of each are shown in Table 3. While stirring the solution dissolved in MDI, the solution dissolved in the monoamine is added, and the mixture is continuously stirred at 100 to 120 ° C for 30 minutes to carry out a reaction, thereby producing a diurea compound in the base oil to obtain a lubricating oil. Sample. The results of measurement of the base oil density, dynamic viscosity, and surface tension used are shown in Table 3. The consistency and centrifugal oil separation of the obtained lubricating oil sample were measured. Further, the normal temperature high-speed lubricating oil test shown below was carried out, and the life of the high-temperature lubricating oil at normal temperature was measured. The measurement results are summarized in Table 3. Comparative Example 9 to Comparative Example 1 1 A base oil and lithium stearate were blended at a ratio shown in Table 3 to prepare a lubricating oil sample. The same items as in Example 10 were measured for the base oil and lubricating oil samples used. The results are summarized in Table 3. -34 - 200848503 &lt;Normal temperature high-speed lubricating oil test-Deep groove ball bearing (6204)> In Example 1 实施, Example 13 and Comparative Example 9, copper cyanide bath (copper cyanide, sodium cyanide, Potassium hydroxide, 50 to 60 ° C), metal plating treatment is applied to the inner diameter of the inner ring of the deep groove ball bearing (6204) and the inner diameter of the outer ring, thus forming a test bearing. The resulting coating has a thickness of about 20 // m. In Example 1 1 , Example 12 and Comparative Example 1, 7.36 g of tricresyl phosphate was diluted with 2-propanol to prepare 200 ml of a tricresyl phosphate solution, and a deep groove ball bearing (6204) was used. The inner and outer rings were immersed in the solution for 2 hours (solution temperature: 60 ° C), whereby a metal phosphate film was formed on the surface to prepare a test bearing. In Comparative Example 1 1 to Comparative Example 1 3, a deep groove ball bearing (6204) in which a film was not formed was used as a test bearing. The lubricating oil sample shown in Table 3, 0.023 5 g (about 0.5 vol% of the total volume of the bearing) was placed on the raceway surface to seal the test bearing, and the non-contact seal was applied to prepare each test bearing. The test bearing load was loaded with a shaft load of 67 0 N and a radial load of 67 N, and rotated at a rotational speed of 10000 r pm under a normal temperature environment, and the time until the occurrence of the burnt bit was measured as the life time of the lubricating oil. In this endurance test, the product of the pitch diameter dm (mm) of the bearing and the number of revolutions N (rpm) (dmN値) was 340,000. &lt;Normal temperature high-speed lubricating oil test-beveled ball bearing&gt; In Comparative Example 9, a copper cyanide bath (cyanide cyanide, sodium cyanide, potassium hydroxide, 50 to 60 ° C) was used for the bevel ball The outer diameter of the inner ring and the outer diameter of the outer ring of the bearing (outer diameter 150 mm X inner diameter 100 mm, inner and outer ring SUJ2, rotary body 13/32吋 tantalum nitride-35-200848503 ball) are metal plated. Test bearing. The thickness of the coating formed is about 20 # m. In Example 1 1 and Comparative Example 10, 7.3 6 g of tricresyl phosphate was diluted with 2-propanol to prepare 200 ml of a tricresyl phosphate solution, and the inner and outer rings of the bevel ball bearing (same as above) were impregnated. In the solution for 2 hours (solution temperature: 60 ° C), a metal phosphate film was formed on the surface to prepare a test bearing. In Comparative Example 1 1 to Comparative Example 1 3, a bevel ball bearing (the same as the above) in which a film was not formed was used as a test bearing. 3.0 g of the lubricating oil sample shown in Table 3 (about 1% by volume of the entire volume of the bearing) was placed on the raceway surface, and the test bearings were sealed, and non-contact sealing was performed to prepare each test bearing. Under the constant pressure of the test bearing with a pressure of 1 · 8 GPa, the bearing was cooled by the outer cylinder cooling to keep the outer ring of the bearing below 5 〇 t and rotated at a rotational speed of 1 4 00 rpm. The time until the occurrence of burnt bite was measured as the life time of the lubricating oil. In this endurance test, the product of the pitch diameter dm (mm) of the bearing and the number of revolutions N (rpm) (dmN 値) was 185 禹. • 36- 200848503 [Table 3] Example Comparative Example 10 11 12 13 9 10 11 12 13 Lubricating oil blending (% by weight) Base oil synthetic hydrocarbon oil 1] 62 46.5 60 46 46 46 57 46.5 Ester oil 2) 33 46.5 - 32 46 46 46 31 46.5 Derivative Diphenyl Ether Oil 3) - - 93 - - - - Base Oil Density (g/cm3) 0.86 0.88 0.93 0.86 0.88 0.88 0.88 0.86 0.88 40°C base oil dynamic viscosity (mm2/ Sec) 23 19 22 23 19 19 19 22 19 Base oil surface tension at 25 ° C (mN/m) 31.5 30.5 35.4 31.5 30.5 30.5 30.5 31.5 30.5 Thickener lithium stearate 8 8 8 Monoamine: octylamine 2.5 2.8 2.8 - - - - 6.1 2.8 Monoamine: Cyclohexylamine - 3.5 - - - - - Monoamine: p-toluidine - 0.6 0.6 0.6 Diisocyanate: mdi4) 2.5 3.6 3.6 4.5 - - - 5.9 3.6 (Lubricating oil Total) 100 100 100 100 100 100 100 100 100 Consistency 300 290 290 270 290 290 290 260 290 Centrifugal oil separation % 28 18 20 16 38 38 38 7 18 Mineral copper treatment one - Yes - - - - Phosphate coating treatment - There is a - there - - - normal temperature high speed lubricant life h 6204 bearing, dmN = 340,000 &gt; 2000 &gt; 2000 &gt; 2000 &gt; 2000 430 460 210 550 1530 Bevel ball bearing, dmN=1.8 million - &gt;2000 - - 140 180 50 320 260 1) Density 0·83 g/cm3, 4 (TC dynamic viscosity 30 nW/sec, Nippon Steel Chemical Co., Ltd., Xinfu Road Special 601

2) 密度0.92 g/cm3，40°C動黏度12 mm2/Sec，汽巴特殊化學品製，雷歐路普DOS 3) 密度0·93 g/cm3，40°C動黏度22 mm2/Sec，松村石油硏究所製，摩列斯科哈依路 普 LB222) Density 0.92 g/cm3, 40°C dynamic viscosity 12 mm2/Sec, Ciba Specialty Chemicals, Leopold DOS 3) Density 0·93 g/cm3, 40°C dynamic viscosity 22 mm2/Sec, Matsumura Oil Research Institute, Moresko Hayupup LB22

4) 曰本聚氛酯工業製，密利歐最特MT 從表3可知，本發明所使用的潤滑油較佳爲：（1 ) 在4 0 °C的動黏度爲1 5 m m 2 / s e c〜3 0 m m 2 / s e c的基油中， -37- 200848503 含有3重量％以上9重量％未滿之脲系增稠劑；（2 )脲系 增稠劑的單胺成分，是相對於單胺全體含有5 0莫耳％以上 的選自脂肪族單胺及脂環式單胺中至少1種單胺之單胺成 分；（3 )基油的表面張力爲 25 mN/m以上，且密度爲 0.95 g/cm3以下；基油係合成烴油、酯油、烷基二苯醚油 或其等的混合油。又（4 )進一步對軸承軌道環實施表面 處理則更佳。 &lt;實施例1 4〜實施例1 7，比較例1 6及比較例1 7所使用的 潤滑油試料的製作&gt; 在表4所示的基油的一半量中，依表4所示的比例溶 入MDI，在剩下一半的基油中，溶入MDI2倍當量的單 胺。各個的配合比例及種類如表4所示。 邊將溶入MDI的溶液攪拌，邊將溶入單胺的溶液加 入後，以100〜120°C持續攪拌30分鐘以進行反應，藉此 在基油中生成二脲化合物而製得潤滑油試料。所使用的基 油密度、動黏度、表面張力的測定結果顯示於表4。測定 所製得的潤滑油試料之稠度及離心離油度。又進行以下所 示的常溫高速潤滑油試驗，測定常溫高速潤滑油壽命時 間。測定結果整理於表4。 &lt;比較例14及比較例15所使用的潤滑油試料的製作〉 將基油和硬脂酸鋰以表4所示的比例配合而製得潤滑 油試料。對於所使用的基油和潤滑油試料，係測定和實施 -38- 200848503 例1 4同樣的項目。結果整理於表4。 實施例1 4〜實施例1 7、比較例1 4及比較例i 6 使用表4所示的潤滑油試料，進行以下所示的 速潤滑油試驗-深槽滾珠軸承（6 2 0 4 )。潤、滑、油_ 記載於表4。這時的深槽滾珠軸承（6204 )，帛？采 圖所示的冠型的PA樹脂保持器（PA66 + GF25重量 在袋孔部設置凹部的儲油部，在包含該凹部的緣部 球的接觸部全部都進行去角加工。 實施例1 5、比較例1 4及比較例1 6 使用表4所示的潤滑油試料，進行以下所示的 速潤滑油試驗-斜角滾珠軸承。潤滑油壽命一倂記 4。這時的斜角滾珠軸承，係採用第3圖所示的機 型的酚樹脂保持器，在袋孔部的4隅角設置凹部 部，在袋孔部的軸方向兩端設置凹部的儲油部，對 緣部實施去角加工。 比較例1 5及比較例1 7 使用表4所示的潤滑油試料，進行以下所示的 速潤滑油試驗-深槽滾珠軸承（6 2 0 4 )以及常溫高 油試驗-斜角滾珠軸承。潤滑油壽命一倂記載於表 &lt;常溫高速潤滑油試驗-深槽滾珠軸承（6 2 0 4 ) &gt; 常溫高 命一倂 用第5 ：% )， 之與鋼 常溫高 載於表 械加工 的離隙 凹部的 吊溫筒 速潤滑 4 〇 -39- 200848503 將潤滑油試料〇.〇235g(軸承全空間容積的約0.5體 積％ )對準滾道面而封入深槽滾珠軸承（6204 )，實施非 接觸密封而作成各個試驗軸承。讓試驗軸承負荷軸荷重 670N和徑荷重67N，在常溫環境下以1 0000 rpm的旋轉速 度旋轉，測定迄燒咬發生爲止的時間作爲潤滑油壽命時 間。該耐久試驗中，軸承的節圓直徑dm ( mm )和轉數N (rpm )的乘積（dmN値）爲3 5萬。 &lt;常溫高速潤滑油試驗-斜角滾珠軸承&gt; 將潤滑油試料3.0g (軸承全容積的約10%體積）對準 滾道面而封入斜角滾珠軸承（外徑 1 5 0 m m X內徑1 0 0 m m，內外環S U J 2，轉動體1 3 / 3 2吋的氮化矽球），實施 非接觸密封而作成各個試驗軸承。在對試驗軸承用1.8 GPa的定壓加壓下，藉由外筒冷卻將軸承冷卻以使軸承外 環保持在50°C以下，並以1 4500 rpm的旋轉速度進行旋 轉。測定迄燒咬發生爲止的時間作爲潤滑油壽命時間。該 耐久試驗中，軸承的節圓直徑 dm ( mm )和轉數 N (rpm )的乘積（dmN値）爲1 85萬。 -40- 200848503 實施例 比較例 14 15 16 17 14 15 16 17 潤滑油配合(重量％) 基油 合成烴油υ 62 46.5 60 46 46 57 57 酯油2) 33 46.5 - 32 46 46 31 31 院基二苯基醚油3) - - 93 - - - - 基油密度(g/cm3) 0.86 0.88 0.93 0.86 0.88 0.88 0.86 0.86 40°C的基油動黏度(mm2/sec) 23 19 22 23 19 19 22 22 25°C的基油表面張力(mN/m) 31.5 30.5 35.4 31.5 30.5 30.5 31.5 31.5 增稠劑 硬脂酸鋰 8 8 單胺:辛胺 2.5 2.8 2.8 - - - 6.1 6.1 單胺:環己胺 - - - 4.5 - - - - 單胺:對甲苯胺 - 0.6 0.6 二異氰酸酯:mdi4) 2.5 3.6 3.6 3.5 - - 5.9 5.9 (潤滑油配合合計） 100 100 100 100 100 100 100 100 稠度 300 290 290 270 290 290 260 260 離心離油度％ 28 18 20 16 38 38 7 7 冠型保持器加工5)之有無(無用「-」表示） 有 有 有 有 有 - 有 - 常溫高速潤滑油壽命h(深槽滾珠軸 承，dmN=35 萬） &gt;2000 &gt;2000 &gt;2000 &gt;2000 380 210 640 550 機械加工型保持器加工6)之有無(無 用表示） - 有 - - 有 - 有 - 常溫高速潤滑油壽命h(斜角滾珠軸 承，dmN=185 萬） - &gt;2000 一 - 240 50 410 320 [表4] 1) 密度〇·83 g/cm3 ’ 40°C動黏度30 mm2/sec，新日鐵化學製，新福路特6014) 曰本聚酯酯制制制密密密特特MT From Table 3, the lubricating oil used in the present invention is preferably: (1) The dynamic viscosity at 40 ° C is 15 mm 2 / sec Among the base oils of ~30 mm 2 / sec, -37-200848503 contains 3% by weight or more and 9% by weight of the urea thickener which is less than full; (2) the monoamine component of the urea thickener is relative to the single The amine contains 50 mol% or more of a monoamine component selected from at least one monoamine of an aliphatic monoamine and an alicyclic monoamine; (3) the surface tension of the base oil is 25 mN/m or more, and the density It is 0.95 g/cm3 or less; the base oil is a mixed oil of a synthetic hydrocarbon oil, an ester oil, an alkyl diphenyl ether oil or the like. Further, (4) it is more preferable to further perform surface treatment on the bearing orbital ring. &lt;Example 1 4 to Example 1 7 , Comparative Example 1 6 and Comparative Example 1 Preparation of Lubricating Oil Sample Used in &gt; In half of the amount of the base oil shown in Table 4, as shown in Table 4 The ratio is dissolved in MDI, and in the remaining half of the base oil, two equivalents of monoamine of MDI are dissolved. The matching ratios and types of each are shown in Table 4. While stirring the solution dissolved in the MDI, the solution in which the monoamine is dissolved is added, and the mixture is continuously stirred at 100 to 120 ° C for 30 minutes to carry out a reaction, thereby producing a diurea compound in the base oil to prepare a lubricating oil sample. . The results of measurement of the base oil density, dynamic viscosity, and surface tension used are shown in Table 4. The consistency and centrifugal oil separation of the obtained lubricating oil sample were measured. Further, the normal temperature high-speed lubricating oil test shown below was carried out, and the life of the high-temperature lubricating oil at normal temperature was measured. The measurement results are summarized in Table 4. &lt;Preparation of Lubricating Oil Samples Used in Comparative Example 14 and Comparative Example 15> A lubricating oil sample was prepared by blending a base oil and lithium stearate in the ratios shown in Table 4. For the base oil and lubricant samples used, the same items as in Example 1-4 of -38-200848503 were measured and implemented. The results are summarized in Table 4. Example 1 4 to Example 1 7. Comparative Example 1 4 and Comparative Example i 6 Using the lubricating oil sample shown in Table 4, the following quick lubricant test - deep groove ball bearing (6 2 0 4 ) was carried out. Run, slip, and oil _ are described in Table 4. At this time, the deep groove ball bearing (6204), what? The crown type PA resin holder shown in the drawing (the PA66 + GF25 weight is provided in the oil reservoir of the recessed portion in the pocket portion, and the contact portion of the edge ball including the recess portion is subjected to the chamfering process. Example 1 Comparative Example 1 4 and Comparative Example 1 6 The lubricating oil sample shown in Table 4 was used, and the speed lubricating oil test shown below - a bevel ball bearing was used. The life of the lubricating oil was 4, and the bevel ball bearing at this time was In the phenol resin holder of the model shown in Fig. 3, the concave portion is provided at the four corners of the bag hole portion, and the oil storage portion of the concave portion is provided at both axial ends of the bag hole portion, and the edge portion is chamfered. Comparative Example 1 5 and Comparative Example 1 7 Using the lubricating oil sample shown in Table 4, the following quick lubricant test was carried out - deep groove ball bearing (6 2 0 4 ) and normal temperature high oil test - bevel ball Bearings. Lubricant life is listed in the table &lt;Normal temperature high-speed lubricant test - deep groove ball bearing (6 2 0 4 ) &gt; normal temperature and high life with the fifth: %), and the steel at room temperature is high on the table Lubricated cylinder lubrication of machined recessed recesses 4 〇-39- 200848503 〇.〇235g material (bearing member about 0.5% by volume of the whole space volume) and the rolling surface aligned sealed deep groove ball bearing (6204), the implementation of non-contact seal and bearings made of each test. The test bearing load was loaded with a load of 670 N and a load of 67 N in a normal temperature environment at a rotation speed of 100,000 rpm, and the time until the occurrence of the burnt bit was measured as the life time of the lubricating oil. In this endurance test, the product of the pitch diameter dm (mm) of the bearing and the number of revolutions N (rpm) (dmN値) was 350,000. &lt;Normal temperature high-speed lubricating oil test-oblique-angle ball bearing&gt; A lubricating oil sample of 3.0 g (about 10% by volume of the full volume of the bearing) is aligned with the raceway surface to seal the bevel ball bearing (outer diameter of 150 mm X) Each of the test bearings was formed by performing non-contact sealing with a diameter of 1 0 0 mm, inner and outer rings SUJ 2, and a rotating body of 1 3 / 3 2 turns of tantalum nitride balls. The bearing was cooled by external cylinder cooling under constant pressure of 1.8 GPa for the test bearing to keep the bearing outer ring below 50 ° C and rotated at a rotational speed of 1 4500 rpm. The time until burnt bite occurred was measured as the life time of the lubricating oil. In this endurance test, the product of the pitch diameter dm (mm) of the bearing and the number of revolutions N (rpm) (dmN値) was 18.5 million. -40- 200848503 EXAMPLES Comparative Example 14 15 16 17 14 15 16 17 Lubricating oil blending (% by weight) Base oil synthetic hydrocarbon oil υ 62 46.5 60 46 46 57 57 Ester oil 2) 33 46.5 - 32 46 46 31 31 Diphenyl ether oil 3) - - 93 - - - - Base oil density (g/cm3) 0.86 0.88 0.93 0.86 0.88 0.88 0.86 0.86 40 °C base oil dynamic viscosity (mm2/sec) 23 19 22 23 19 19 22 22 25 ° C base oil surface tension (mN / m) 31.5 30.5 35.4 31.5 30.5 30.5 31.5 31.5 thickener lithium stearate 8 8 monoamine: octylamine 2.5 2.8 2.8 - - - 6.1 6.1 monoamine: cyclohexylamine - - - 4.5 - - - - Monoamine: p-toluidine - 0.6 0.6 Diisocyanate: mdi4) 2.5 3.6 3.6 3.5 - - 5.9 5.9 (total of lubricating oil) 100 100 100 100 100 100 100 100 Consistency 300 290 290 270 290 290 260 260 Centrifugal oil separation % 28 18 20 16 38 38 7 7 Crown retainer processing 5) With or without ("" indicates) There are some - Yes - Normal temperature high speed lubricant life h (deep groove ball Bearing, dmN=350,000) &gt;2000 &gt;2000 &gt;2000 &gt;2000 380 210 640 550 Machining type cage processing 6) With or without (useless meter) ) - Yes - - Yes - Yes - Normal temperature high speed lubricant life h (oblique ball bearing, dmN = 1.85 million) - &gt;2000 One - 240 50 410 320 [Table 4] 1) Density 〇·83 g/cm3 ' 40 ° C dynamic viscosity 30 mm2 / sec, Nippon Steel Chemical System, Xinfu Road 601

2) 密度0.92 g/cm3，40°C動黏度12 mm2/sec，汽巴特殊化學品製，雷歐路普DOS 3 )密度〇·93 g/cm3，40°C動黏度22 mm2/sec，松村石油硏究所製，摩列斯科哈依路 普 LB222) Density 0.92 g/cm3, 40°C dynamic viscosity 12 mm2/sec, Ciba Specialty Chemicals, Leopold DOS 3) Density 〇·93 g/cm3, 40°C dynamic viscosity 22 mm2/sec, Matsumura Oil Research Institute, Moresko Hayupup LB22

4) 曰本聚氨醋工業製，密利歐聶特MT 5) 形成儲油部，去角施工 6) 形成儲油部，形成離隙，去角施工 -41 - 200848503 從表4可知，本發明所使用的潤滑油較佳爲：（1 ) 在40°C的動黏度爲15 mm2/sec〜30 mm2/sec的基油中’ 含有3重量％以上9重量％未滿之脲系增稠劑；（2 )脲系 增稠劑的單胺成分，是相對於單胺全體含有5 0莫耳％以上 的選自脂肪族單胺及脂環式單胺中至少1種單胺之單胺成 分；（3 )基油的表面張力爲25 mN/m以上，且密度爲 0.95 g/cm3以下；基油係合成烴油、酯油、烷基二苯醚油 或其等的混合油。又（4 )進一步在軸承的樹脂保持器的 袋孔部設置凹部的儲油部、離隙部等等，並實施去角加工 則更佳。 實施例1 8〜實施例2 1、比較例2 0 在表5所示的基油的一半量中，依表5所示的比例溶 入M DI，在剩下一半的基油中，溶入 M D I 2倍當量的單 胺。各個的配合比例及種類如表5所示。 邊將溶入MDI的溶液攪拌，邊將溶入單胺的溶液加 入後，以100〜12(TC持續攪拌30分鐘以進行反應，藉此 在基油中生成二脲化合物而製得潤滑油試料。所使用的基 油密度、動黏度、表面張力的測定結果顯示於表2。測定 所製得的潤滑油試料之稠度及離心離油度。 在實施以下所示撥油劑處理的滾動軸承，將所製得的 潤滑油試料封入，進行以下所示的常溫高速潤滑油試驗， 測定常溫高速潤滑油壽命時間。測定結果整理於表5。 -42- 200848503 &lt;撥油劑處理&gt; 在密封構件的軸承內部側表面塗布氟系的撥 理劑（LION製，Rain Guard)，在室溫下乾燥1 作成滾動軸承（深槽滾珠軸承，軸承尺寸：外徑 內徑2 0 m m X寬1 4 m m ;斜角滾珠軸承，軸承尺 150 mmx 內徑 1〇〇 mmx 寬 24 mm)。 &lt;常溫高速潤滑油試驗-深槽滾珠軸承（6 0 2 4 ) &gt; 將潤滑油試料0.023 5 g (軸承全空間容積的; 積％ )對準滾道面而封入深槽滾珠軸承（6〇24 ) 接觸密封而作成各個試驗軸承。讓試驗軸承負 670N和徑荷重67N，在常溫環境下以loooo rpm 度旋轉，測定迄燒咬發生爲止的時間作爲潤滑 間。該耐久試驗中，軸承的節圓直徑d m ( m m ) (rpm )的乘積（dmN値）爲3 5萬。 &lt;常溫高速潤滑油試驗-斜角滾珠軸承&gt; 將實施例1 9、比較例1 8〜比較例2 1的潤 3.0 g (軸承全容積的約1 〇 %體積）對準滾道面而 滾珠軸承（外徑1 5 0 m m X內徑1 0 0 m m，內外環 動體13/32吋的氮化矽球），實施非接觸密封而 試驗軸承。在對試驗軸承用1 · 8 GPa的定壓加壓 外筒冷卻將軸承冷卻以使軸承外環保持在5 0 °C以 1 4 5 00 rpm的旋轉速度進行旋轉。測定迄燒咬發 水撥油處 小時，而 4 7 m m X 寸：外徑4) 曰 聚 聚 工业 , , , , MT MT MT MT MT MT MT MT MT MT MT MT MT MT MT MT MT MT MT MT MT MT MT MT MT MT MT MT MT MT MT MT MT MT MT MT MT MT MT MT MT MT MT MT MT MT MT The lubricating oil used in the invention is preferably: (1) in a base oil having a dynamic viscosity of 15 mm 2 /sec to 30 mm 2 /sec at 40 ° C 'containing more than 3% by weight and 9% by weight of urea-based thickening (2) The monoamine component of the urea-based thickener is a monoamine containing at least one monoamine selected from the group consisting of an aliphatic monoamine and an alicyclic monoamine with respect to the entire monoamine. (3) The base oil has a surface tension of 25 mN/m or more and a density of 0.95 g/cm3 or less; and the base oil is a mixed oil of a synthetic hydrocarbon oil, an ester oil, an alkyl diphenyl ether oil or the like. Further, (4) it is more preferable to provide the oil storage portion, the relief portion, and the like of the concave portion in the pocket portion of the resin holder of the bearing, and perform the chamfering process. Example 1 8 to Example 2 1. Comparative Example 2 0 In half the amount of the base oil shown in Table 5, MDI was dissolved in the ratio shown in Table 5, and dissolved in the remaining half of the base oil. MDI 2 equivalents of monoamine. The proportions and types of each are shown in Table 5. While stirring the solution dissolved in MDI, the solution in which the monoamine was dissolved was added, and the reaction was carried out at 100 to 12 (TC was continuously stirred for 30 minutes to carry out a reaction, thereby producing a diurea compound in the base oil to prepare a lubricating oil sample. The measurement results of the base oil density, dynamic viscosity, and surface tension used are shown in Table 2. The consistency of the obtained lubricating oil sample and the centrifugal oil separation were measured. The rolling bearing treated with the following oil-repellent agent was The obtained lubricating oil sample was sealed, and the normal temperature high-speed lubricating oil test shown below was carried out, and the normal-temperature high-speed lubricating oil life time was measured. The measurement results are shown in Table 5. -42 - 200848503 &lt;oil-removing agent treatment&gt; The inner side surface of the bearing is coated with a fluorine-based conditioner (LION Guard, Rain Guard), which is dried at room temperature to make a rolling bearing (deep groove ball bearing, bearing size: outer diameter inner diameter 2 0 mm X width 14 mm; Bevel ball bearing, bearing ruler 150 mmx inner diameter 1〇〇mmx width 24 mm). &lt;Normal temperature high-speed lubricant test-Deep groove ball bearing (6 0 2 4 ) &gt; Lubricating oil sample 0.023 5 g (bearing full Space volume Align the raceway surface and seal the deep groove ball bearing (6〇24) into the test bearing to make each test bearing. Let the test bearing have a negative 670N and a radial load of 67N, and rotate at loooo rpm under normal temperature to measure the occurrence of burnt bite. The time until the time is used as the lubrication room. In the endurance test, the product of the pitch diameter dm (mm) (rpm) of the bearing (dmN値) is 350,000. &lt;Normal temperature high-speed lubricating oil test-angled ball bearing&gt; Example 1 9. Comparative Example 1 8 to Comparative Example 2 The wetness of 3.0 g (about 1 〇% of the total volume of the bearing) was aligned with the raceway surface and the ball bearing (outer diameter 150 mm X inner diameter 1 0 0 Mm, inner and outer ring-shaped moving body 13/32吋 nitrided ball), test bearing by non-contact sealing. In the test bearing, pressurize the outer cylinder with a constant pressure of 1 · 8 GPa to cool the bearing to make the bearing outer ring Rotate at a rotation speed of 1 4 5 00 rpm at 50 ° C. Measure the hour after the bite of water and oil, and 4 7 mm X inch: outer diameter

約〇·5體 ，實施非 荷軸荷重 的旋轉速 油爵命時 和轉數N 滑油試料 封入斜角 SUJ2 ，轉 作成各個 下，藉由 下，並以 生爲止的 -43- 200848503 時間作爲潤滑油壽命時間。該耐久試驗中，軸承的節圓直 徑 dm(mm)和轉數N(rpm)的乘積（dmN値）爲185 萬。 比較例1 8 將基油和硬脂酸鋰依表5所示的比例配合而製得潤滑 '油試料。測定所使用的基油的表面張力。對所得的潤滑油 試料’測定稠度，並進行上述的離心油分離試驗而測定離 心離油度。將所得的潤滑油試料封入實施上述撥油劑處理 後的滾動軸承，進行上述的常溫高速潤滑油試驗，測定常 溫局速潤滑油壽命時間。測定結果一併顯示於表5。 比較例1 9 將基油和硬脂酸鋰依表5所示的比例配合而製得潤滑 油試料。測定所使用的基油的表面張力。對所得的潤滑油 試料’測定稠度，並進行上述的離心油分離試驗而測定離 心離油度。將所得的潤滑油試料封入未實施上述撥油劑處 理的滾動軸承，進行上述的常溫高速潤滑油試驗，測定常 溫高速潤滑油壽命時間。測定結果一倂顯示於表5。 比較例2 1 依表5所示的配合比例進行和實施例1 8同樣的處理 而製得潤滑油試料。測定所使用的基油的表面張力。對所 得的潤滑油試料，測定稠度，並進行上述的離心油分離試 -44 - 200848503 驗而測定離心離油度。將所得的潤滑油試料封入未實施上 述撥油劑處理的滾動軸承，進行上述的常溫高速潤滑油試 驗，測定常溫高速潤滑油壽命時間。測定結果一倂顯示於 表5。 -45- 200848503 m 5]About 5·5 body, the non-loading load of the rotating speed oil and the number of revolutions N oil sample sealed into the oblique angle SUJ2, converted into each, by the next, and the time of -43-200848503 Lubricant life time. In this endurance test, the product of the pitch diameter dm (mm) of the bearing and the number of revolutions N (rpm) (dmN値) was 1.85 million. Comparative Example 1 8 A lubricating oil sample was prepared by blending a base oil and lithium stearate in the proportions shown in Table 5. The surface tension of the base oil used was measured. The obtained lubricating oil sample was measured for consistency, and the centrifugal oil separation test described above was carried out to measure the centrifugal oil separation. The obtained lubricating oil sample was sealed in a rolling bearing subjected to the above-described oil-repellent treatment, and the above-mentioned normal temperature high-speed lubricating oil test was carried out to measure the service life of the normal-temperature local-speed lubricating oil. The measurement results are shown together in Table 5. Comparative Example 1 9 A lubricating oil sample was prepared by blending a base oil and lithium stearate in the proportions shown in Table 5. The surface tension of the base oil used was measured. The obtained lubricating oil sample was measured for consistency, and the centrifugal oil separation test described above was carried out to measure the centrifugal oil separation. The obtained lubricating oil sample was sealed in a rolling bearing which was not subjected to the above-described oil-repellent treatment, and the above-mentioned normal temperature high-speed lubricating oil test was carried out to measure the normal-temperature high-speed lubricating oil life time. The results of the measurement are shown in Table 5. Comparative Example 2 1 A lubricating oil sample was obtained by the same treatment as in Example 18 in accordance with the mixing ratio shown in Table 5. The surface tension of the base oil used was measured. For the obtained lubricating oil sample, the consistency was measured, and the centrifugal oil separation was measured by the above-mentioned centrifugal oil separation test -44 - 200848503. The obtained lubricating oil sample was sealed in a rolling bearing which was not subjected to the above-described oil-repellent treatment, and the above-mentioned normal temperature high-speed lubricating oil test was carried out to measure the normal-temperature high-speed lubricating oil life time. The results of the measurement are shown in Table 5. -45- 200848503 m 5]

實施例 比較例 18 19 20 21 18 19 20 21 潤滑油配合(重量％) 基油 合成烴油1} 62 46.5 - 60 46 46 57 57 酯油2) 33 46.5 - 32 46 46 31 31 烷基二苯基醚油3) - - 93 - - - - 基油密度(g/cm3) 0.86 0.88 0.93 0.86 0.88 0.88 0.86 0.86 40°C的基油動黏度(mm2/sec) 23 19 22 23 19 19 22 22 25X：的基油表面張力(mN/m) 31.5 30.5 35.4 31.5 30.5 30.5 31.5 31.5 增稠劑 硬脂酸鋰 8 8 單胺:辛胺 2.5 2.8 2.8 - 一 一 6.1 6.1 單胺:環己胺 - - — 3.5 - - 一 — 單胺:對甲苯胺 一 0.6 0.6 二異氰酸酯:mdi4) 2.5 3.6 3.6 4.5 一 — 5.9 5.9 (潤滑油配合合計） 100 100 100 100 100 100 100 100 稠度 300 290 290 270 290 290 260 260 離心離油度。/。 28 18 20 16 38 38 7 7 撥油劑處理之有無（「-」表示無處理） 有 有 有 有 有 — 有 - 常溫高速潤滑油壽命h 深槽滾珠軸承(6204)，dmN=35萬 &gt;2000 &gt;2000 &gt;2000 &gt;2000 460 210 820 550 斜角滾珠軸承，dmN=185萬 - &gt;2000 - - 340 50 510 320 1 )密度0·83 g/cm3，40°C動黏度30 mm2/SeC，新日鐵化學製，新福路特601 2)密度0.92 g/cm3，4(TC動黏度12 mm2/sec，汽巴特殊化學品製，雷歐路普DOS 3 )密度0.93 g/cm3，40°C動黏度22 mm2/SeC，松村石油硏究所製，摩列斯科哈依路 普 LB22 4)曰本聚氨酯工業製，密利歐聶特MT 從表5可知，本發明所使用的潤滑油較佳爲：（1 ) 在4〇°C的動黏度爲1 5 mm2/sec〜30 mm2/sec的基油中， 含有3重量％以上9重量％未滿之脲系增稠劑；（2 )脲系 -46- 200848503 增稠劑的單胺成分，是相對於單胺全體含有5 0莫耳％以上 的選自脂肪族單胺及脂環式單胺中至少1種單胺之單胺成 分；（3)基油的表面張力爲 25 mN/m以上，且密度爲 0.95 g/cm3以下；基油係合成烴油、酯油、烷基二苯醚油 或其等的混合油。又（4 )進一步在與潤滑油接觸之軸承 內部表面的至少一部分形成撥水撥油性被膜則更佳。 本發明之將高速軸承用潤滑油封入內部之高速用滾動 軸承，由於封入的潤滑油，是在具有既定動黏度的基油中 配合既定量的增稠劑（含有既定量脂肪族成分之脲系化合 物），故在高速旋轉下的軸承耐久壽命拉長。又，藉由實 施（1 )在選自上述內環的滾道面表面、外環的滾道面表 面及轉動體的表面中至少一個實施凹坑加工，（2 )在選 自上述內環的外徑面、外環的內徑面、轉動體的表面中至 少一個形成被膜，（3 )在上述保持器的袋孔部配設凹部 的儲油部、離隙部，並進行去角加工，（4 )在與潤滑油 接觸之軸承內部表面的至少一部分形成撥水撥油性被膜等 等，可進一步延長高速旋轉下的軸承耐久壽命。 因此，適用於作爲組裝在可高速滑動旋轉的工作機械 的主軸之滾動軸承，該工作機械包括：車床、鑽床、搪 床、銑床、磨床、搪光機、超精密加工機、硏光機等等。 而且，和油氣潤滑法等的連續供應潤滑油的方式不同，由 於將潤滑油封入內部來使用，可減低運轉成本，且謀求省 空間化。 -47- 200848503 【圖式簡單說明】 第1圖係本發明的高速用滾動軸承的一實施形態之斜 角滾珠軸承的截面圖。 第2圖係本發明的高速用滾動軸承的另一實施形態之 斜角滾珠軸承的截面圖。 第3圖係斜角滾珠軸承所使用的機械加工型保持器的 立體圖。 第4圖係本發明的高速用滾動軸承的其他實施形態之 深槽滾珠軸承的縱截面圖。 第5圖係深槽滾珠軸承所使用的冠型保持器之立體 圖。 第6圖係本發明的高速用滾動軸承的其他實施形態之 斜角滾珠軸承的撥水撥油性被膜的形成位置一例之截面 圖。 第7圖係上述撥水撥油性被膜的形成位置的其他例的 截面圖。 弟8圖係上述撥水撥油性被膜的形成位置的其他例的 截面圖。 第9圖係上述撥水撥油性被膜的形成位置的其他例的 截面圖。 第1 〇圖係和上述同樣的實施形態之深槽滾珠軸承的 撥水撥油性被膜的形成位置一例的截面圖。 第 Π圖係上述撥水撥油性被膜的形成位置的其他例 的截面圖。 -48- 200848503 第1 2圖係上述撥水撥油性被膜的形成位置的其他例 的截面圖。 第〗3圖係上述撥水撥油性被膜的形成位置的其他例 的截面圖。 第1 4圖係斜角滾珠軸承的截面圖。 【主要元件符號說明】 1、 1 1、3 1、5 1 :斜角滾動軸承 2、 12、 32、 52:內環 3、 13、 33、 53:外環 4、 14、3 4、5 4 :轉動體（鋼球） 5、 1 5、3 5、5 5 :保持器 6、 1 6、3 6 :密封構件 7 =潤滑油袋孔 1 5 a :袋孔部內面 1 5 b :離隙部 1 5 c :儲油部 1 5 d :凹部的緣部 8 、 17、 27、 37、 47:潤滑油 2 1、4 1 :深槽滾珠軸承 22、42 :內環 2 3、4 3 :外環 24、 44 :轉動體 25、 45 :保持器 -49 - 200848503 2 5 a :袋孔部內面 2 5 b :交叉面側儲油部 2 5 c :底面側儲油部 2 5 d :凹部的緣部 2 6、4 6 :密封構件 3 8 a、3 8 b、3 8 c、3 8 d :撥水撥油性被膜 4 2 a :內環滾道面 43a :外環滾道面 4 8 a、4 8 b、4 8 c、4 8 d :撥水撥油性被膜EXAMPLES Comparative Example 18 19 20 21 18 19 20 21 Lubricating oil blending (% by weight) Base oil synthetic hydrocarbon oil 1} 62 46.5 - 60 46 46 57 57 Ester oil 2) 33 46.5 - 32 46 46 31 31 Alkyl diphenyl Base ether oil 3) - - 93 - - - - Base oil density (g/cm3) 0.86 0.88 0.93 0.86 0.88 0.88 0.86 0.86 40 °C base oil dynamic viscosity (mm2/sec) 23 19 22 23 19 19 22 22 25X : Base oil surface tension (mN/m) 31.5 30.5 35.4 31.5 30.5 30.5 31.5 31.5 Thickener lithium stearate 8 8 Monoamine: octylamine 2.5 2.8 2.8 - 11.1 6.1 Monoamine: Cyclohexylamine - - 3.5 - - a - monoamine: p-toluidine - 0.6 0.6 diisocyanate: mdi4) 2.5 3.6 3.6 4.5 a - 5.9 5.9 (total of lubricating oil) 100 100 100 100 100 100 100 100 Consistency 300 290 290 270 290 290 260 260 Centrifugal oil separation. /. 28 18 20 16 38 38 7 7 Whether or not the oil remover is treated ("-" means no treatment) Yes or No - Yes - Normal temperature high speed lubricant life h Deep groove ball bearing (6204), dmN = 350,000> 2000 &gt;2000 &gt;2000 &gt;2000 460 210 820 550 Bevel ball bearing, dmN=1.8 million - &gt;2000 - - 340 50 510 320 1) Density 0·83 g/cm3, 40°C dynamic viscosity 30 mm2 /SeC, Nippon Steel Chemical Co., Ltd., Xinfuluote 601 2) Density 0.92 g/cm3, 4 (TC dynamic viscosity 12 mm2/sec, Ciba Specialty Chemicals, Leopold DOS 3) Density 0.93 g/ Cm3, 40°C dynamic viscosity 22 mm2/SeC, manufactured by Matsumura Petroleum Research Institute, Morrisko Hayupup LB22 4) Sakamoto Polyurethane Industrial Co., Ltd., Miriam NTE MT As shown in Table 5, the present invention The lubricating oil to be used is preferably: (1) in a base oil having a dynamic viscosity of 1 5 mm 2 /sec to 30 mm 2 /sec at 4 ° C, containing 3% by weight or more and 9% by weight of urea-based thickening (2) Urea-46-200848503 The monoamine component of the thickener is at least one selected from the group consisting of an aliphatic monoamine and an alicyclic monoamine with respect to the entire monoamine content of 50 mol% or more. Amine monoamine component; (3) The surface tension of the oil is 25 mN / m or more, and a density of 0.95 g / cm3 or less; oil-based synthetic hydrocarbon base oils, ester oils, alkyl diphenyl ether oil, or mixed oil and the like. Further, (4) it is more preferable to form a water-repellent oil-repellent film on at least a part of the inner surface of the bearing which is in contact with the lubricating oil. In the high-speed rolling bearing in which the high-speed bearing lubricating oil is sealed, the lubricating oil enclosed is a predetermined amount of a thickener (a urea compound containing a quantitative aliphatic component) in a base oil having a predetermined dynamic viscosity. Therefore, the bearing durability of the bearing under high-speed rotation is elongated. Further, by performing (1) at least one of a surface of the raceway surface selected from the inner ring, a surface of the raceway surface of the outer ring, and a surface of the rotor, (2) selected from the inner ring At least one of the outer diameter surface, the inner diameter surface of the outer ring, and the surface of the rotor forms a film, and (3) an oil reservoir and a relief portion of the recess are disposed in the pocket portion of the retainer, and the chamfering process is performed. (4) A water-repellent oil-repellent film or the like is formed on at least a part of the inner surface of the bearing which is in contact with the lubricating oil, and the bearing durability life under high-speed rotation can be further prolonged. Therefore, it is suitable for use as a rolling bearing assembled in a spindle of a work machine capable of high-speed sliding rotation, which includes: a lathe, a drill press, a boring machine, a milling machine, a grinder, a calender, an ultra-precision machining machine, a calender, and the like. Further, unlike the method of continuously supplying the lubricating oil such as the oil-air lubrication method, since the lubricating oil is sealed and used, the running cost can be reduced and the space can be saved. -47-200848503 [Brief Description of the Drawings] Fig. 1 is a cross-sectional view showing an oblique-angle ball bearing according to an embodiment of the high-speed rolling bearing of the present invention. Fig. 2 is a cross-sectional view showing a bevel ball bearing according to another embodiment of the high speed rolling bearing of the present invention. Figure 3 is a perspective view of a machined retainer used in a bevel ball bearing. Fig. 4 is a longitudinal sectional view showing a deep groove ball bearing of another embodiment of the high speed rolling bearing according to the present invention. Figure 5 is a perspective view of a crown retainer used in deep groove ball bearings. Fig. 6 is a cross-sectional view showing an example of a position at which a water-repellent oil-repellent film of a bevel ball bearing of another embodiment of the high-speed rolling bearing according to the present invention is formed. Fig. 7 is a cross-sectional view showing another example of the position at which the water-repellent oil-repellent film is formed. Fig. 8 is a cross-sectional view showing another example of the position at which the water-repellent oil-repellent film is formed. Fig. 9 is a cross-sectional view showing another example of the position at which the water-repellent oil-repellent film is formed. Fig. 1 is a cross-sectional view showing an example of a position at which the water-repellent oil-repellent film of the deep groove ball bearing of the above-described embodiment is formed. The first drawing is a cross-sectional view showing another example of the position at which the water-repellent oil-repellent film is formed. -48- 200848503 Fig. 1 is a cross-sectional view showing another example of the position at which the water-repellent oil-repellent film is formed. Fig. 3 is a cross-sectional view showing another example of the position at which the water-repellent oil-repellent film is formed. Figure 14 is a cross-sectional view of a beveled ball bearing. [Description of main component symbols] 1, 1 1, 3 1, 5 1 : Angled rolling bearings 2, 12, 32, 52: Inner rings 3, 13, 33, 53: Outer rings 4, 14, 3 4, 5 4 : Rotating body (steel ball) 5, 1 5, 3 5, 5 5 : retainer 6, 16 6 , 3 6 : sealing member 7 = lubricating oil bag hole 1 5 a : inner surface of bag hole portion 1 5 b : clearance portion 1 5 c : Oil storage part 1 5 d : Edge part of the recess 8 , 17, 27, 37, 47: Lubricating oil 2 1 , 4 1 : Deep groove ball bearing 22, 42 : Inner ring 2 3, 4 3 : Outside Rings 24, 44: Rotating bodies 25, 45: Retainer-49 - 200848503 2 5 a : Inner surface of the pocket portion 2 5 b : Oil reservoir 2 5 c : Oil reservoir at the bottom side 2 5 d : Concave portion Edge portion 2 6 , 4 6 : sealing member 3 8 a, 3 8 b, 3 8 c, 3 8 d : water-repellent oil-coated film 4 2 a : inner ring raceway surface 43a: outer ring raceway surface 4 8 a , 4 8 b, 4 8 c, 4 8 d: water dialing oily film

Claims (1)

200848503 十、申請專利範圍 1 · 一種高速軸承用潤滑油，係含有基油和脲系增稠劑 之高速軸承用潤滑油，其特徵在於： 前述基油在 40 °C的動黏度爲 15 mm2/sec〜30 mm2/sec ； 前述脲系增稠劑是將聚異氰酸酯成分和單胺成分反應 而製得；該單胺成分，是相對於單胺全體含有5 〇莫耳％以 上的選自脂肪族單胺及脂環式單胺中至少1種單胺之單胺 成分； 相對於潤滑油全體，前述脲系增稠劑含量爲3重量％ 以上9重量％未滿。 2·如申請專利範圍第1項記載之高速軸承用潤滑油， 其中，前述基油的表面張力爲25 mN/m以上，且密度爲 0.95 g/cm3 以下。 3 ·如申請專利範圍第1項記載之高速軸承用潤滑油， 其中，前述基油，係選自合成烴油、酯油、烷基二苯醚油 中至少1種油。 4 · 一種高速用滾動軸承，係用來支承以高速旋轉的軸 之高速用滾動軸承，其特徵在於： 該滾動軸承係具備：內環及外環、介設於該內環及外 環間之複數個轉動體、用來保持該轉動體的保持器、將前 述內環及外環間的間隙的開口予以覆蓋之密封構件；在前 述轉動體的周圍封入潤滑油， 前述潤滑油是使用申請專利範圍第1項記載之潤滑 -51 - 200848503 油。 5 .如申請專利範圍第4項記載之高速用滾動軸承，其 中，在選自前述內環的滾道面表面、前述外環的滾道面表 面及前述轉動體的表面中至少一個，實施凹坑加工。 6 .如申請專利範圍第5項記載之高速用滾動軸承，其 中，前述凹坑加工爲珠擊加工，藉由該加工而形成於各表 面的凹坑，從該表面起算的深度爲0.1〜10//m。 7 ·如申請專利範圍第4項記載之高速用滾動軸承，其 中，在選自前述內環的外徑面、前述外環的內徑面以及前 述轉動體的表面中至少一個，形成被膜。 8 .如申請專利範圍第7項記載之高速用滾動軸承，其 中，前述被膜，係藉由金屬鍍敷處理或磷酸被膜處理所形 成的被膜。 9 .如申請專利範圍第4項記載之高速用滾動軸承，其 中，前述保持器，係用袋孔部來保持前述轉動體，在該袋 孔部的內面具有凹部，且至少該凹部的緣部被去角。 1 0.如申請專利範圍第9項記載之高速用滾動軸承， 其中，前述凹部是儲油部或離隙部。 1 1 ·如申請專利範圍第4項記載之高速用滾動軸承， 其中，前述保持器是樹脂製的保持器。 1 2·如申請專利範圍第1 1項記載之高速用滾動軸承， 其中，前述保持器所使用的樹脂，係聚醯胺樹脂、酣樹脂 或聚醚醚酮樹脂。 1 3 ·如申請專利範圍第4項記載之高速用滾動軸承， -52- 200848503 其中，在與前述潤滑油接觸之軸承內¥ 分，形成撥水撥油性被膜。 1 4 ·如申請專利範圍第1 3項記載之 其中，前述撥水撥油性被膜係形成於： 件的軸承內部側表面的一部分、（2 ) 外的內徑面及密封構件的軸承內部側表 除軌道面以外的外徑面及密封構件的| (4 )除與轉動體的接觸面以外之保持 個。 1 5 ·如申請專利範圍第1 3項記載之 其中，前述撥水撥油性被膜，係使用矽 合物來形成。 16.如申請專利範圍第15項記載之 其中’前述矽系化合物是矽氧烷，前述 基砂院。 1 7 .如申請專利範圍第4項記載之 其中，則述局速用滾動軸承，係用來支 的軸承。 1 8 ·如申請專利範圍第4項記載之 其中’前述高速用滾動軸承，是斜角滾 軸承。 β表面的至少一部 局速用滾動軸承， 選自（1 )密封構 外環之除軌道面以 面、（3 )內環之 由承內部側表面、 器的表面中至少一 局速用滾動軸承， 系化合物或氟系化 局速用滾動軸承， 氟系化合物是氟烷 高速用滾動軸承， 承工作機械的主軸 高速用滾動軸承， 珠軸承或圓柱滾子 -53-200848503 X. Patent application scope 1 · A lubricating oil for high-speed bearings, which is a lubricating oil for high-speed bearings containing a base oil and a urea thickener, characterized in that the dynamic viscosity of the base oil at 40 ° C is 15 mm 2 / Sec~30 mm2/sec; The urea-based thickener is obtained by reacting a polyisocyanate component with a monoamine component; the monoamine component is selected from the group consisting of aliphatics and more than 5 mol% per mol of the monoamine. The monoamine component of at least one monoamine of the monoamine and the alicyclic monoamine; and the content of the urea thickener is not more than 3% by weight to 9% by weight based on the total amount of the lubricating oil. 2. The high-speed bearing lubricating oil according to the first aspect of the invention, wherein the base oil has a surface tension of 25 mN/m or more and a density of 0.95 g/cm3 or less. The lubricating oil for a high-speed bearing according to the first aspect of the invention, wherein the base oil is at least one selected from the group consisting of synthetic hydrocarbon oils, ester oils, and alkyl diphenyl ether oils. A high-speed rolling bearing is a high-speed rolling bearing for supporting a shaft that rotates at a high speed, and is characterized in that: the rolling bearing has an inner ring and an outer ring, and a plurality of rotations interposed between the inner ring and the outer ring. a sealing member for holding a retainer of the rotating body and covering an opening between the inner ring and the outer ring; sealing the lubricating oil around the rotating body, the lubricating oil is used in the first patent application range Itemized Lubrication -51 - 200848503 Oil. The high-speed rolling bearing according to claim 4, wherein at least one of the surface of the raceway surface of the inner ring, the surface of the raceway surface of the outer ring, and the surface of the rotor is subjected to a pit. machining. 6. The high-speed rolling bearing according to claim 5, wherein the dimple is processed by beading, and the pit formed on each surface by the processing has a depth of 0.1 to 10/ from the surface. /m. The high-speed rolling bearing according to claim 4, wherein at least one of an outer diameter surface of the inner ring, an inner diameter surface of the outer ring, and a surface of the rotor is formed to form a film. The high-speed rolling bearing according to claim 7, wherein the film is a film formed by metal plating treatment or phosphoric acid film treatment. The high-speed rolling bearing according to claim 4, wherein the holder holds the rotor with a pocket hole portion, and has a concave portion on an inner surface of the pocket portion, and at least an edge portion of the recess portion Was de-horned. The high-speed rolling bearing according to claim 9, wherein the recessed portion is an oil reservoir or a relief portion. The high-speed rolling bearing according to claim 4, wherein the retainer is a resin retainer. The high-speed rolling bearing according to the first aspect of the invention, wherein the resin used in the retainer is a polyamide resin, an anthracene resin or a polyetheretherketone resin. 1 3 - A high-speed rolling bearing according to item 4 of the patent application, -52- 200848503, wherein a water-repellent oil-repellent film is formed in a bearing that is in contact with the lubricating oil. In the above description, the water-repellent oil-repellent film is formed on a part of the inner side surface of the bearing, (2) the outer diameter surface, and the inner side of the bearing of the sealing member. The outer diameter surface other than the raceway surface and the sealing member (4) are held in addition to the contact surface with the rotor. In the above description, the water-repellent oil-repellent film is formed using a compound. 16. The method of claim 15, wherein the lanthanide compound is a lanthanane, the base sandstone. 1 7. In the case of the fourth paragraph of the patent application, the rolling bearing for the local speed is used for the bearing. 1 8 The above-mentioned high-speed rolling bearing is described in the fourth paragraph of the patent application, which is a beveled roller bearing. At least one partial speed rolling bearing on the surface of the β, selected from the group consisting of (1) the outer surface of the outer ring of the sealing outer ring, the inner surface of the inner ring of the inner ring, and the at least one local speed rolling bearing of the inner surface of the inner ring. A compound or a fluorine-based rolling bearing for speed, a fluorine-based compound is a high-speed rolling bearing for fluorocarbon, a high-speed rolling bearing for a spindle of a working machine, a bead bearing or a cylindrical roller-53-
TW097106632A 2007-02-26 2008-02-26 High-speed bearings with lubricating oil and high-speed rolling bearings TWI454568B (en)

Applications Claiming Priority (5)

Application Number Priority Date Filing Date Title
JP2007046258A JP5305600B2 (en) 2007-02-26 2007-02-26 Grease for high-speed bearings and rolling bearings for spindles
JP2007134670A JP2008286372A (en) 2007-05-21 2007-05-21 Rolling bearing for high speed
JP2007171804A JP2009008209A (en) 2007-06-29 2007-06-29 High-speed rolling bearing
JP2007198443A JP2009036221A (en) 2007-07-31 2007-07-31 High-speed rolling bearing
JP2007293879A JP2009121531A (en) 2007-11-13 2007-11-13 Rolling bearing for high speed

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TWI454568B TWI454568B (en) 2014-10-01

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