JP2005098316A - Conical roller bearing - Google Patents

Conical roller bearing Download PDF

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Publication number
JP2005098316A
JP2005098316A JP2003329794A JP2003329794A JP2005098316A JP 2005098316 A JP2005098316 A JP 2005098316A JP 2003329794 A JP2003329794 A JP 2003329794A JP 2003329794 A JP2003329794 A JP 2003329794A JP 2005098316 A JP2005098316 A JP 2005098316A
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Japan
Prior art keywords
cage
roller bearing
outer ring
tapered roller
diameter surface
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Withdrawn
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JP2003329794A
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Japanese (ja)
Inventor
Takashi Tsujimoto
崇 辻本
Toshiaki Azuma
敏昭 東
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NTN Corp
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NTN Corp
NTN Toyo Bearing Co Ltd
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Priority to JP2003329794A priority Critical patent/JP2005098316A/en
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C19/00—Bearings with rolling contact, for exclusively rotary movement
    • F16C19/22—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings
    • F16C19/34—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load
    • F16C19/36—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load with a single row of rollers
    • F16C19/364—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load with a single row of rollers with tapered rollers, i.e. rollers having essentially the shape of a truncated cone
    • 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
    • F16C33/46—Cages for rollers or needles
    • F16C33/4605—Details of interaction of cage and race, e.g. retention or centring
    • 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
    • F16C33/46—Cages for rollers or needles
    • F16C33/467—Details of individual pockets, e.g. shape or roller retaining means
    • F16C33/4676—Details of individual pockets, e.g. shape or roller retaining means of the stays separating adjacent cage pockets, e.g. guide means for the bearing-surface of the rollers
    • 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
    • F16C2240/00—Specified values or numerical ranges of parameters; Relations between them
    • F16C2240/40—Linear dimensions, e.g. length, radius, thickness, gap
    • 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
    • F16C2240/00—Specified values or numerical ranges of parameters; Relations between them
    • F16C2240/40—Linear dimensions, e.g. length, radius, thickness, gap
    • F16C2240/70—Diameters; Radii
    • 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
    • F16C2240/00—Specified values or numerical ranges of parameters; Relations between them
    • F16C2240/40—Linear dimensions, e.g. length, radius, thickness, gap
    • F16C2240/70—Diameters; Radii
    • F16C2240/80—Pitch circle diameters [PCD]
    • F16C2240/82—Degree of filling, i.e. sum of diameters of rolling elements in relation to PCD
    • F16C2240/84—Degree of filling, i.e. sum of diameters of rolling elements in relation to PCD with full complement of balls or rollers, i.e. sum of clearances less than diameter of one rolling element
    • 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
    • F16C2361/00—Apparatus or articles in engineering in general
    • F16C2361/61—Toothed gear systems, e.g. support of pinion shafts
    • 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
    • F16C33/46—Cages for rollers or needles
    • F16C33/4617—Massive or moulded cages having cage pockets surrounding the rollers, e.g. machined window cages
    • F16C33/4623—Massive or moulded cages having cage pockets surrounding the rollers, e.g. machined window cages formed as one-piece cages, i.e. monoblock cages
    • F16C33/4635—Massive or moulded cages having cage pockets surrounding the rollers, e.g. machined window cages formed as one-piece cages, i.e. monoblock cages made from plastic, e.g. injection moulded window cages
    • 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
    • F16C33/46—Cages for rollers or needles
    • F16C33/54—Cages for rollers or needles made from wire, strips, or sheet metal
    • F16C33/542—Cages for rollers or needles made from wire, strips, or sheet metal made from sheet metal
    • F16C33/543—Cages for rollers or needles made from wire, strips, or sheet metal made from sheet metal from a single part
    • 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
    • F16C33/6637—Special parts or details in view of lubrication with liquid lubricant
    • F16C33/6681—Details of distribution or circulation inside the bearing, e.g. grooves on the cage or passages in the rolling elements
    • 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
    • F16C33/6696—Special parts or details in view of lubrication with solids as lubricant, e.g. dry coatings, powder

Abstract

<P>PROBLEM TO BE SOLVED: To provide a conical roller bearing increasing the number of rollers without lowering stiffness of a retainer, and besides suppressing increase in torque as much as possible. <P>SOLUTION: In this conical roller bearing 1 provided with an inner ring 2, an outer ring 3, two or more conical rollers 4 arranged rotatably between the inner ring 2 and the outer ring 3, and the retainer 5 retaining the conical rollers 4 at predetermined circumferential intervals, two or more projections 5f having circular arc cross sections, which are projected toward the inner diameter surface of the outer ring 3 and form a minute clearance between the outer diameter surface of the pole part of the retainer 5 and the inner diameter surface of the outer ring 3 are formed on the outer diameter surface of the pole part of the retainer 5 at predetermined circumferential intervals. <P>COPYRIGHT: (C)2005,JPO&NCIPI

Description

この発明は円錐ころ軸受に関し、特に自動車のトランスミッションの歯車装置に好適に組み込まれる円錐ころ軸受に関する。   The present invention relates to a tapered roller bearing, and more particularly to a tapered roller bearing that is suitably incorporated in a gear device of an automobile transmission.

自動車のトランスミッション（主変速機）は大別するとマニュアルタイプとオートマチックタイプがあり、また車輌の駆動方式によって前輪駆動（ＦＷＤ）用トランスアクスル、後輪駆動（ＲＷＤ）用トランスミッション、および四輪駆動（４ＷＤ）用トランスファ（副変速機）がある。これらは、エンジンからの駆動力を変速して駆動軸などへ伝達するものである。   Automobile transmissions (main transmissions) are broadly classified into manual types and automatic types. Depending on the vehicle drive system, front wheel drive (FWD) transaxle, rear wheel drive (RWD) transmission, and four wheel drive (4WD) ) Transfer (sub-transmission). These shift the driving force from the engine and transmit it to the drive shaft or the like.

図６は、自動車 のトランスミッションの一構成例を示している。このトランスミッションは同期噛合式のもので、同図で左方向がエンジン側、右方向が駆動車輪側である。メインシャフト４１とメインドライブギヤ４２との間に円錐ころ軸受 ４３が介装される。この例では、メインドライブギヤ４２の内周に円錐ころ軸受 ４３の外輪軌道面が直接形成されている。メインドライブギヤ４２は、円錐ころ軸受 ４４でケーシング４５に対して回転自在に支持される。メインドライブギヤ４２にクラッチギヤ４６が係合連結され、クラッチギヤ４６に近接してシンクロ機構４７が配設される。   FIG. 6 shows an example of the configuration of an automobile transmission. This transmission is of a synchronous mesh type, and in the figure the left direction is the engine side and the right direction is the drive wheel side. A tapered roller bearing 43 is interposed between the main shaft 41 and the main drive gear 42. In this example, the outer ring raceway surface of the tapered roller bearing 43 is formed directly on the inner periphery of the main drive gear 42. The main drive gear 42 is rotatably supported with respect to the casing 45 by a tapered roller bearing 44. A clutch gear 46 is engaged and connected to the main drive gear 42, and a synchronization mechanism 47 is disposed in the vicinity of the clutch gear 46.

シンクロ機構４７は、セレクタ（図示省略）の作動によって軸方向（同図で左右方向）に移動するスリーブ４８と、スリーブ４８の内周に軸方向移動自在に装着されたシンクロナイザーキー４９と、メインシャフト４１の外周に係合連結されたハブ５０と、クラッチギヤ４６の外周（コーン部）に摺動自在に装着されたシンクロナイザーリング５１と、シンクロナイザーキー４９をスリーブ４８の内周に弾性的に押圧する押さえピン５２及びスプリング５３とを備えている。   The synchronizer 47 includes a sleeve 48 that moves in the axial direction (left and right in the figure) by the operation of a selector (not shown), a synchronizer key 49 that is mounted on the inner periphery of the sleeve 48 so as to be axially movable, A hub 50 engaged and connected to the outer periphery of the shaft 41, a synchronizer ring 51 slidably mounted on the outer periphery (cone portion) of the clutch gear 46, and a synchronizer key 49 are elastically attached to the inner periphery of the sleeve 48. A pressing pin 52 and a spring 53 are provided.

同図に示す状態では、スリーブ４８及びシンクロナイザーキー４９が押さえピン５２によって中立位置に保持されている。この時、メインドライブギヤ４２はメインシャフト４１に対して空転する。一方、セレクタの作動により、スリーブ４８が同図に示す状態から例えば軸方向左側に移動すると、スリーブ４８に従動してシンクロナイザーキー４９が軸方向左側に移動し、シンクロナイザーリング５１をクラッチギヤ４６のコーン部の傾斜面に押し付ける。これにより、クラッチギヤ４６の回転速度が落ち、逆にシンクロ機構４７側の回転速度が高められる。そして、両者の回転速度が同期した頃、スリーブ４８がさらに軸方向左側に移動して、クラッチギヤ４６と噛み合い、メインシャフト４１とメインドライブギヤ４２との間がシンクロ機構４７を介して連結される。これにより、メインシャフト４１とメインドライブギヤ４２とが同期回転する。   In the state shown in the figure, the sleeve 48 and the synchronizer key 49 are held in the neutral position by the pressing pin 52. At this time, the main drive gear 42 idles with respect to the main shaft 41. On the other hand, when the sleeve 48 is moved to the left side in the axial direction, for example, by the operation of the selector, the synchronizer key 49 is moved to the left side in the axial direction following the sleeve 48, and the synchronizer ring 51 is moved to the clutch gear 46. Press against the inclined surface of the cone. As a result, the rotational speed of the clutch gear 46 decreases, and conversely, the rotational speed on the synchro mechanism 47 side is increased. When the rotational speeds of the two are synchronized, the sleeve 48 further moves to the left in the axial direction, meshes with the clutch gear 46, and the main shaft 41 and the main drive gear 42 are connected via the sync mechanism 47. . Thereby, the main shaft 41 and the main drive gear 42 rotate synchronously.

ところで、自動車トランスミッションは、近年、ミッションのＡＴ化、ＣＶＴ化および低燃費化等のために低粘度の油が使われる傾向にある。低粘度オイルが使用される環境化では、（１）油温が高い、（２）油量が少ない、（３）予圧抜けが発生するなどの悪条件が重なった場合に、潤滑不良に起因する非常に短寿命の表面起点剥離が面圧の高い内輪軌道面に生じることがある。   By the way, in recent years, low-viscosity oil tends to be used for automobile transmissions in order to achieve mission AT, CVT, fuel efficiency, and the like. In an environment where low-viscosity oil is used, it is caused by poor lubrication when adverse conditions such as (1) high oil temperature, (2) low oil volume, and (3) preload loss occur. Very short-life surface-origin separation may occur on the inner ring raceway surface with high surface pressure.

この表面起点剥離による短寿命対策としては最大面圧低減が直接的かつ有効な解決策である。最大面圧を低減するためには軸受寸法を変更するか、軸受寸法を変えない場合は軸受のころ本数を増大させる。ころ直径を減少させないでころ本数を増やすためには保持器のポケット間隔を狭くしなければならないが、そのためには保持器のピッチ円を大きくして外輪側にできるだけ寄せる必要がある。   As a countermeasure for short life due to this surface-origin separation, reduction of the maximum surface pressure is a direct and effective solution. In order to reduce the maximum surface pressure, the bearing dimensions are changed, or if the bearing dimensions are not changed, the number of rollers of the bearing is increased. In order to increase the number of rollers without reducing the roller diameter, the pocket interval of the cage must be narrowed. For this purpose, it is necessary to enlarge the pitch circle of the cage and bring it closer to the outer ring side as much as possible.

保持器を外輪内径面に接するまで寄せた例として、図７に記載の円錐ころ軸受がある（特許文献１参照）。この円錐ころ軸受６１は保持器６２の小径側環状部６２ａの外周面と大径側環状部６２ｂの外周面を外輪６３内径面と摺接させて保持器６２をガイドし、保持器６２の柱部６２ｃの外径面に引きずりトルクを抑制するため凹所６４を形成して、柱部６２ｃの外径面と外輪６３の軌道面６３ａの非接触状態を維持するようにしている。保持器６２は詳しくは図８に示すように、小径側環状部６２ａと、大径側環状部６２ｂと、小径側環状部６２ａと大径側環状部６２ｂとを軸方向に繋ぎ外径面に凹所６４が形成された複数の柱部６２ｃとを有する。そして柱部６２ｃ相互間に円錐ころ６５を転動自在に収容するための複数のポケット６６が設けられている。小径側環状部６２ａには、内径側に一体に延びた鍔部６２ｄが設けられている。
特開２００３−２８１６５号公報 As an example in which the cage is brought into contact with the inner surface of the outer ring, there is a tapered roller bearing shown in FIG. 7 (see Patent Document 1). The tapered roller bearing 61 guides the cage 62 by sliding the outer peripheral surface of the small-diameter side annular portion 62 a and the outer peripheral surface of the large-diameter side annular portion 62 b with the inner surface of the outer ring 63. A recess 64 is formed in the outer diameter surface of the portion 62c to suppress drag torque, and the non-contact state between the outer diameter surface of the column portion 62c and the raceway surface 63a of the outer ring 63 is maintained. As shown in detail in FIG. 8, the retainer 62 has a small-diameter-side annular portion 62a, a large-diameter-side annular portion 62b, a small-diameter-side annular portion 62a, and a large-diameter-side annular portion 62b connected in the axial direction to the outer diameter surface. And a plurality of column portions 62c in which recesses 64 are formed. A plurality of pockets 66 are provided between the column portions 62c for accommodating the tapered rollers 65 in a rollable manner. The small-diameter-side annular portion 62a is provided with a flange portion 62d that extends integrally on the inner-diameter side.
JP 2003-28165 A

特許文献１記載の円錐ころ軸受６１では、保持器６２の柱部６２ｃに凹所６４があるので板厚が必然的に薄くなって保持器６２の剛性が低下し、軸受６１の組立て時の応力によって保持器６２が変形したり、軸受６１の回転中に保持器６２が変形する等の可能性がある。また保持器６２の小径側環状部６２ａの外周面と大径側環状部６２ｂの外周面を外輪６３内径面と摺接させているためその分だけ高トルクになるという問題もある。   In the tapered roller bearing 61 described in Patent Document 1, since the recess 64 is provided in the column portion 62 c of the cage 62, the plate thickness is inevitably thinned, the rigidity of the cage 62 is reduced, and the stress during assembly of the bearing 61 is reduced. Due to this, there is a possibility that the cage 62 is deformed or the cage 62 is deformed while the bearing 61 is rotating. Further, since the outer peripheral surface of the small-diameter side annular portion 62a and the outer peripheral surface of the large-diameter side annular portion 62b of the cage 62 are in sliding contact with the inner surface of the outer ring 63, there is a problem that the torque is increased accordingly.

本発明の目的は、保持器剛性を低下させることなくころ収容本数を増大可能であって、しかもトルクの増大を可及的に抑制可能な円錐ころ軸受を提供することにある。   An object of the present invention is to provide a tapered roller bearing that can increase the number of rollers accommodated without lowering the rigidity of the cage and can suppress an increase in torque as much as possible.

前記目的を達成するため本発明の円錐ころ軸受（請求項１）は、内輪と、外輪と、前記内輪と外輪との間に転動自在に配された複数の円錐ころと、前記円錐ころを円周所定間隔に保持する保持器とを備えた円錐ころ軸受において、前記保持器の外径面に、前記外輪の内径面に向かって凸状をなし前記外輪の内径面との間に微小隙間を形成する突起部を円周所定間隔で複数形成したことを特徴とする。   In order to achieve the above object, a tapered roller bearing according to the present invention (Claim 1) includes an inner ring, an outer ring, a plurality of tapered rollers arranged to roll between the inner ring and the outer ring, and the tapered roller. In the tapered roller bearing provided with a cage that holds at a predetermined circumferential interval, the outer diameter surface of the cage is convex toward the inner diameter surface of the outer ring, and a minute gap is formed between the inner diameter surface of the outer ring and the outer ring. A plurality of protrusions that form the shape are formed at predetermined intervals around the circumference.

前記突起部を形成することにより円錐ころ軸受の回転時に突起部と外輪内径面との間に形成される楔状油膜の動圧により保持器と外輪との間の微小隙間が維持され、両者の接触に伴うトルク損失や保持器ないし外輪軌道面の損傷が防止される。従って保持器外径面を可及的に外輪内径面に接することなく近接させることが可能となり、軸受トルクを増大させることなく保持器のころ収容本数を増大させて内輪軌道面に生じる最大面圧を抑制することができる。   By forming the protrusion, a minute gap between the cage and the outer ring is maintained by the dynamic pressure of the wedge-shaped oil film formed between the protrusion and the inner diameter surface of the outer ring when the tapered roller bearing rotates. Torque loss and damage to the cage or outer ring raceway surface are prevented. Accordingly, the outer diameter surface of the cage can be brought as close as possible without contacting the inner diameter surface of the outer ring, and the maximum surface pressure generated on the inner ring raceway surface can be increased by increasing the number of rollers accommodated in the cage without increasing the bearing torque. Can be suppressed.

また本発明の円錐ころ軸受（請求項２）は、前記突起部が保持器の柱部外径面に断面円弧状で形成され、その円弧曲率半径が外輪軌道面の半径よりも小さく、かつ、前記突起部の幅寸法を保持器の柱部の幅寸法の５０％以上としたことを特徴とする。
突起部の形を、外輪軌道面の半径よりも小さい曲率半径の断面円弧状とし、突起部の幅寸法を保持器の柱部の幅寸法の５０％以上とすることにより、軸受回転時に外輪内径面との間に良好な楔状油膜が形成され、この楔状油膜の動圧により保持器と外輪との非接触状態が維持される。 Further, in the tapered roller bearing of the present invention (Claim 2), the protrusion is formed in an arc shape in cross section on the outer diameter surface of the column portion of the cage, the arc curvature radius is smaller than the radius of the outer ring raceway surface, and The width dimension of the protrusion is 50% or more of the width dimension of the column part of the cage.
The shape of the protrusion is an arc of cross section with a radius of curvature smaller than the radius of the outer ring raceway surface, and the width of the protrusion is 50% or more of the width of the cage pillar, so that the inner diameter of the outer ring is A good wedge-shaped oil film is formed between the surface and the non-contact state between the cage and the outer ring by the dynamic pressure of the wedge-shaped oil film.

また本発明の円錐ころ軸受（請求項３）は、保持器が鋼板プレス製であることを特徴とする。鋼板プレス製保持器は高剛性であり耐摩耗性があるので軸受寿命の延長に適する。   The tapered roller bearing according to the present invention (Claim 3) is characterized in that the cage is made of a steel plate press. Steel plate press cages are highly rigid and wear resistant, making them suitable for extending bearing life.

また本発明の円錐ころ軸受（請求項４、５）は、前記保持器の外周面が二硫化モリブデン（MoS2）系でコーティング処理またはバレル研磨されていることを特徴とする。 The tapered roller bearing according to the present invention (claims 4 and 5) is characterized in that the outer peripheral surface of the cage is coated or barrel-polished with a molybdenum disulfide (MoS 2 ) system.

このような平滑化処理をすることにより軸受起動時のトルク損失や保持器摩耗を低減することができる。   By performing such a smoothing process, it is possible to reduce torque loss and cage wear at the start of the bearing.

また本発明の円錐ころ軸受（請求項６）は、前記保持器がＰＰＳ、ＰＥＥＫ、ＰＰＡまたはポリアミド樹脂製であることを特徴とする。
樹脂製保持器は鋼板プレス製保持器と比べると重量が軽く摩擦係数が小さいため、軸受起動時のトルク損失や保持器摩耗の低減に好適である。 The tapered roller bearing according to the present invention (claim 6) is characterized in that the cage is made of PPS, PEEK, PPA or polyamide resin.
Since the resin cage is lighter and has a smaller friction coefficient than the steel plate press cage, it is suitable for reducing torque loss and cage wear at the start of the bearing.

本発明は前述の如く、円錐ころ軸受の保持器の外周面に外輪の内周面に向かって凸状をなす突起部を円周所定間隔で複数形成したので、保持器外径面を外輪内径面に近接させてころ収容本数を増大させても、突起部と外輪内周面との間で楔状油膜による良好な潤滑作用が得られる。従って、軸受のトルク特性を損なうことなくころ本数増大によって内外輪軌道面の最大面圧を低減させることができ、高油温、少油量、および予圧抜け発生など悪条件が重なって過酷潤滑条件となった場合でも、極短寿命の表面起点剥離がとりわけ内輪軌道面に発生するのを防止することができる。   In the present invention, as described above, a plurality of protrusions that are convex toward the inner peripheral surface of the outer ring are formed on the outer peripheral surface of the retainer of the tapered roller bearing at predetermined circumferential intervals. Even if the number of rollers accommodated is increased by being close to the surface, a good lubricating action by the wedge-shaped oil film can be obtained between the protrusion and the inner peripheral surface of the outer ring. Therefore, the maximum surface pressure of the inner and outer ring raceways can be reduced by increasing the number of rollers without impairing the torque characteristics of the bearing, and the adverse conditions such as high oil temperature, small amount of oil, and occurrence of preload loss can overlap with severe lubrication conditions. Even in this case, it is possible to prevent the occurrence of surface-origin separation having an extremely short life, particularly on the inner ring raceway surface.

以下に本発明の一実施形態を図に基づいて説明する。図１および図４に示す如く、この実施形態の円錐ころ軸受１は、円錐状の軌道面２ａを有し、この軌道面２ａの小径側に小鍔部２ｂ、大径側に大鍔部２ｃを有する内輪２と、円錐状の軌道面３ａを有する外輪３と、内輪２の軌道面２ａと外輪３の軌道面３ａとの間に転動自在に配された複数の円錐ころ４と、円錐ころ４を円周等間隔に保持する保持器５とで構成される。   Hereinafter, an embodiment of the present invention will be described with reference to the drawings. As shown in FIGS. 1 and 4, the tapered roller bearing 1 of this embodiment has a conical raceway surface 2a, and a small flange portion 2b on the small diameter side of the raceway surface 2a and a large flange portion 2c on the large diameter side. , An outer ring 3 having a conical raceway surface 3a, a plurality of tapered rollers 4 disposed between the raceway surface 2a of the inner ring 2 and the raceway surface 3a of the outer ring 3, and a cone It is comprised with the holder | retainer 5 which hold | maintains the roller 4 at the circumference equal intervals.

保持器５は、例えばＳＰＣＣ鋼板等の鋼板（鋼管）からプレス加工によって成形されたプレス加工品で、図３に示すように、小径側環状部５ａと、大径側環状部５ｂと、小径側環状部５ａと大径側環状部５ｂとを軸方向に繋ぐ複数の柱部５ｃと、円周方向に隣接する柱部５ｃ間に設けられ、円錐ころ４を転動自在に収容する複数のポケット５ｄとを備えている。小径側環状部５ａには、内径側に一体に延びた鍔部５ｅが設けられている。   The cage 5 is a press-worked product formed by pressing from a steel plate (steel pipe) such as an SPCC steel plate, for example, as shown in FIG. 3, a small-diameter side annular portion 5a, a large-diameter side annular portion 5b, and a small-diameter side. A plurality of pockets that are provided between a plurality of column portions 5c that connect the annular portion 5a and the large-diameter-side annular portion 5b in the axial direction, and a column portion 5c that is adjacent in the circumferential direction, and that accommodate the tapered rollers 4 in a rollable manner. 5d. The small-diameter-side annular portion 5a is provided with a flange portion 5e that extends integrally on the inner-diameter side.

柱部５ｃの外径面には図１〜図３に示すように外輪軌道面側に向けて凸状を成す突起部５ｆが一体に形成されている。この突起部５ｆは図２に示すように柱部５ｃの横断方向の断面輪郭形状が円弧状を成している。この円弧状の曲率半径Ｒ２は外輪軌道面半径Ｒ１より小さく形成されている。これは突起部５ｆと外輪軌道面との間に良好な楔状油膜が形成されるようにするためであり、望ましくは突起部の曲率半径Ｒ２は外輪軌道面半径Ｒ１の７０〜９０％程度に形成するとよい。７０％未満であると楔状油膜の入口開き角度が大きくなり過ぎて却って動圧が低下する。また９０％を超えると楔状油膜の入口角度が小さくなり過ぎて同様に動圧が低下する。また、突起部５ｆの横幅Ｗ２は望ましくは柱部５ｃの横幅Ｗ１の５０％以上となるように形成する（Ｗ２≧０．５×Ｗ１）。５Ｏ％未満では良好な楔状油膜を形成するための充分な突起部５ｆの高さが確保できなくなるためである。なお、外輪軌道面半径Ｒ１は大径側から小径側へと連続的に変化しているので、突起部５ｆの曲率半径Ｒ２もそれに合わせて大径側環状部５ｂの大きな曲率半径Ｒ２から小径側環状部５ａの小さな曲率半径Ｒ２へと連続的に変化するようにする。   As shown in FIGS. 1 to 3, a protruding portion 5 f that is convex toward the outer ring raceway surface is integrally formed on the outer diameter surface of the column portion 5 c. As shown in FIG. 2, the projecting portion 5f has a circular cross-sectional contour shape of the column portion 5c. The arc-shaped curvature radius R2 is smaller than the outer ring raceway radius R1. This is to form a good wedge-shaped oil film between the protrusion 5f and the outer ring raceway surface. Preferably, the curvature radius R2 of the protrusion is formed to be about 70 to 90% of the outer ring raceway radius R1. Good. If it is less than 70%, the opening angle of the wedge-shaped oil film becomes too large, and the dynamic pressure decreases. If it exceeds 90%, the inlet angle of the wedge-shaped oil film becomes too small, and the dynamic pressure similarly decreases. Further, the lateral width W2 of the protruding portion 5f is desirably formed to be 50% or more of the lateral width W1 of the column portion 5c (W2 ≧ 0.5 × W1). This is because if it is less than 5%, a sufficient height of the protrusion 5f for forming a good wedge-shaped oil film cannot be secured. Since the outer ring raceway surface radius R1 continuously changes from the large diameter side to the small diameter side, the curvature radius R2 of the projection 5f is accordingly adjusted from the large curvature radius R2 of the large diameter side annular portion 5b to the small diameter side. It is made to change continuously to the small curvature radius R2 of the annular part 5a.

保持器５の表面、特に保持器５の外径面は、できるだけ滑らかな表面にしておくのがよい。すなわち、円錐ころ軸受１の回転中は保持器５外径面の突起部５ｆと外輪軌道面との間に楔状油膜が形成されてその動圧作用で保持器５の外径面ないし突起部５ｆが外輪軌道面に接触することはないが、円錐ころ軸受１の回転直後で低回転数のため十分な楔状油膜が形成されないうちに過酷な潤滑条件が発生すると保持器５の外径面ないし突起部５ｆが外輪軌道面に接触する可能性がある。このような場合に備えて、保持器５の外径面を例えば二硫化モリブデン（MoS2）系のコーティング処理をしたり、またはバレル研磨仕上げ等を行なうことにより可及的に摩擦係数を低減する処置をしておくのがよい。 The surface of the cage 5, particularly the outer diameter surface of the cage 5, should be as smooth as possible. That is, during rotation of the tapered roller bearing 1, a wedge-shaped oil film is formed between the protrusion 5f on the outer diameter surface of the cage 5 and the outer ring raceway surface, and the dynamic pressure action causes the outer diameter surface or the protrusion 5f of the cage 5. Does not come into contact with the outer ring raceway surface, but the outer diameter surface or protrusion of the retainer 5 is generated when severe lubricating conditions occur before the wedge roller oil film is formed due to the low rotational speed immediately after the tapered roller bearing 1 rotates. There is a possibility that the portion 5f contacts the outer ring raceway surface. In preparation for such a case, the friction coefficient is reduced as much as possible by coating the outer diameter surface of the cage 5 with, for example, molybdenum disulfide (MoS 2 ) coating or barrel polishing. It is better to take treatment.

保持器５は鋼板プレス製品のほか、樹脂製の保持器５’（図５参照）としてもよい。この樹脂製保持器５’の柱部５’ｃ外径面にも、鋼板プレス製保持器５と同様に突起部５’ｆを一体形成する。樹脂の種類としては、自動車トランスミッションでの使用を前提する場合は耐油性を考慮してＰＰＳ、ＰＥＥＫ、ＰＰＡ等のスーパーエンプラ又はポリアミド樹脂とするのが望ましい。樹脂製保持器５’は鋼板プレス製保持器５と比べると重量が軽く摩擦係数が小さいという特徴があるため、本発明の円錐ころ軸受用保持器として好適である。   The cage 5 may be a resin-made cage 5 '(see FIG. 5) in addition to a steel plate press product. A protruding portion 5 ′ f is integrally formed on the outer diameter surface of the column portion 5 ′ c of the resin cage 5 ′ in the same manner as the steel plate press cage 5. As the type of resin, it is desirable to use super engineering plastics such as PPS, PEEK, PPA, or polyamide resin in consideration of oil resistance when used in an automobile transmission. The resin cage 5 'is suitable as the tapered roller bearing cage of the present invention because it has a feature that it is lighter and has a smaller friction coefficient than the steel plate press cage 5.

本発明の円錐ころ軸受１は以上にように構成されているため、軸受１が回転して保持器５（５’）が回転し始めると、外輪軌道面と保持器５（５’）の突起部５ｆとの間に楔状油膜が形成される。この楔状油膜は軸受１の回転速度にほぼ比例した動圧を発生するので、保持器５（５’）のピッチ円直径（ＰＣＤ）を大きくして外輪軌道面に近接させても、軸受１を大きな摩耗ないしトルク損失を生じることなく回転させることが可能となり、無理なくころ本数を増加させることが可能となる。   Since the tapered roller bearing 1 of the present invention is configured as described above, when the bearing 1 rotates and the cage 5 (5 ′) starts to rotate, the outer ring raceway surface and the projection of the cage 5 (5 ′) are obtained. A wedge-shaped oil film is formed between the portion 5f. Since this wedge-shaped oil film generates a dynamic pressure substantially proportional to the rotational speed of the bearing 1, even if the pitch circle diameter (PCD) of the retainer 5 (5 ') is increased and brought close to the outer ring raceway surface, the bearing 1 is maintained. It is possible to rotate without causing great wear or torque loss, and it is possible to increase the number of rollers without difficulty.

以上、本発明の一実施形態につき説明したが、本発明は前記実施形態に限定されることなく種々の変形が可能である。例えば前記実施形態では突起部５ｆ（５’ｆ）を柱部５ｃ（５’ｃ）の外径面に形成したが、これに加えて、保持器５（５’）の小径側環状部５ａや大径側環状部５ｂの外径面にも形成することができる。   Although one embodiment of the present invention has been described above, the present invention is not limited to the above embodiment, and various modifications can be made. For example, in the above-described embodiment, the protrusion 5f (5′f) is formed on the outer diameter surface of the column 5c (5′c), but in addition to this, the small-diameter side annular portion 5a of the cage 5 (5 ′) It can also be formed on the outer diameter surface of the large-diameter side annular portion 5b.

本発明に係る円錐ころ軸受１ は、自動車のトランスミッションに組み込む他、自動車のデファレンシャルや、自動車用歯車装置以外の用途に使用することも可能である。   The tapered roller bearing 1 according to the present invention can be used for applications other than automobile differentials and automobile gears, in addition to being incorporated in automobile transmissions.

本発明に係る円錐ころ軸受の部分断面図。The fragmentary sectional view of the tapered roller bearing which concerns on this invention. 保持器の柱部の断面図。Sectional drawing of the pillar part of a holder | retainer. 保持器の部分斜視図。The fragmentary perspective view of a holder | retainer. （Ａ）は鋼板プレス製保持器を使用した円錐ころ軸受の縦断面図、（Ｂ）は（Ａ）のＢ−Ｂ線矢視断面図。(A) is a longitudinal cross-sectional view of a tapered roller bearing using a steel plate press cage, and (B) is a cross-sectional view taken along line BB in (A). （Ａ）は樹脂製保持器を使用した円錐ころ軸受の縦断面図、（Ｂ）は（Ａ）のＢ−Ｂ線矢視断面図。(A) is a longitudinal cross-sectional view of a tapered roller bearing using a resin cage, and (B) is a cross-sectional view taken along line BB in (A). 自動車のトランスミッションの部分断面図。The fragmentary sectional view of the transmission of a car. 従来の円錐ころ軸受の部分断面図。The fragmentary sectional view of the conventional tapered roller bearing. 従来の円錐ころ軸受の保持器の斜視図。The perspective view of the retainer of the conventional tapered roller bearing.

符号の説明Explanation of symbols

１ 軸受
２ 内輪
２ａ 軌道面
２ｂ 小鍔部
２ｃ 大鍔部
３ 外輪
３ａ 軌道面
４ 円錐ころ
５ 保持器
５ａ 小径側環状部
５ｂ 大径側環状部
５ｃ 柱部
５ｄ ポケット
５ｅ 鍔部
５ｆ 突起部


DESCRIPTION OF SYMBOLS 1 Bearing 2 Inner ring 2a Raceway surface 2b Small collar part 2c Large collar part 3 Outer ring 3a Raceway surface 4 Tapered roller 5 Cage 5a Small diameter side annular part 5b Large diameter side annular part 5c Pillar part 5d Pocket 5e Groove part 5f Projection part


Claims (6)

内輪と、外輪と、前記内輪と外輪との間に転動自在に配された複数の円錐ころと、前記円錐ころを円周所定間隔に保持する保持器とを備えた円錐ころ軸受において、前記保持器の外径面に、前記外輪の内径面に向かって凸状をなし前記外輪の内径面との間に微小隙間を形成する突起部を円周所定間隔で複数形成したことを特徴とする円錐ころ軸受 。   In the tapered roller bearing comprising an inner ring, an outer ring, a plurality of tapered rollers arranged to roll between the inner ring and the outer ring, and a cage for holding the tapered rollers at a predetermined circumferential interval, A plurality of protrusions that are convex toward the inner diameter surface of the outer ring and that form minute gaps with the inner diameter surface of the outer ring are formed at predetermined circumferential intervals on the outer diameter surface of the cage. Tapered roller bearings. 前記突起部が保持器の柱部外径面に断面円弧状で形成され、その円弧曲率半径が外輪軌道面の半径よりも小さく、かつ、前記突起部の幅寸法を保持器の柱部の幅寸法の５０％以上としたことを特徴とする請求項１記載の円錐ころ軸受 。   The protrusion is formed in a cross-section arc shape on the outer diameter surface of the pillar portion of the cage, the radius of curvature of the arc is smaller than the radius of the outer ring raceway surface, and the width dimension of the projection portion is the width of the pillar portion of the cage. The tapered roller bearing according to claim 1, wherein the tapered roller bearing is 50% or more of the size. 前記保持器が鋼板プレス製であることを特徴とする請求項１記載の円錐ころ軸受 。   The tapered roller bearing according to claim 1, wherein the cage is made of a steel plate press. 前記保持器の外周面が二硫化モリブデン（MoS2）系でコーティング処理されていることを特徴とする請求項１記載の円錐ころ軸受 。 The tapered roller bearing according to claim 1, wherein the outer peripheral surface of the cage is coated with a molybdenum disulfide (MoS 2 ) system. 前記保持器の外周面がバレル研磨されていることを特徴とする請求項１記載の円錐ころ軸受 。   The tapered roller bearing according to claim 1, wherein an outer peripheral surface of the cage is barrel-polished. 前記保持器がＰＰＳ、ＰＥＥＫ、ＰＰＡまたはポリアミド樹脂製であることを特徴とする請求項１記載の円錐ころ軸受 。


The tapered roller bearing according to claim 1, wherein the cage is made of PPS, PEEK, PPA, or polyamide resin.


JP2003329794A 2003-09-22 2003-09-22 Conical roller bearing Withdrawn JP2005098316A (en)

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WO2005111446A1 (en) * 2004-05-13 2005-11-24 Ntn Corporation Tapered roller bearing
WO2007046263A1 (en) * 2005-10-19 2007-04-26 Ntn Corporation Roller bearing
WO2007049450A1 (en) * 2005-10-26 2007-05-03 Ntn Corporation Tapered roller bearing
DE102007044901A1 (en) * 2007-09-19 2009-04-09 Ab Skf Cage i.e. window cage, for roller bearing e.g. cylinder roller bearing, has guiding surface provided in outer and/or inner upper surface area of bar units such that surfaces of units pass into area increasing from surface to bar centre
JP2012107765A (en) * 2012-03-12 2012-06-07 Ntn Corp Tapered roller bearing
JP2016153664A (en) * 2015-02-20 2016-08-25 Ntn株式会社 Conical roller bearing
CN106917817A (en) * 2015-12-17 2017-07-04 株式会社捷太格特 Taper roll bearing

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WO2005111446A1 (en) * 2004-05-13 2005-11-24 Ntn Corporation Tapered roller bearing
US8783965B2 (en) 2004-05-13 2014-07-22 Ntn Corporation Tapered roller bearing
WO2007046263A1 (en) * 2005-10-19 2007-04-26 Ntn Corporation Roller bearing
JP2007120576A (en) * 2005-10-26 2007-05-17 Ntn Corp Tapered roller bearing
WO2007049450A1 (en) * 2005-10-26 2007-05-03 Ntn Corporation Tapered roller bearing
DE102007044901A1 (en) * 2007-09-19 2009-04-09 Ab Skf Cage i.e. window cage, for roller bearing e.g. cylinder roller bearing, has guiding surface provided in outer and/or inner upper surface area of bar units such that surfaces of units pass into area increasing from surface to bar centre
DE102007044901B4 (en) * 2007-09-19 2016-02-25 Ab Skf Cylindrical roller bearing cage and roller bearing
JP2012107765A (en) * 2012-03-12 2012-06-07 Ntn Corp Tapered roller bearing
JP2016153664A (en) * 2015-02-20 2016-08-25 Ntn株式会社 Conical roller bearing
WO2016132983A1 (en) * 2015-02-20 2016-08-25 Ntn株式会社 Tapered roller bearing
CN107429745A (en) * 2015-02-20 2017-12-01 Ntn株式会社 Taper roll bearing
US10267357B2 (en) 2015-02-20 2019-04-23 Ntn Corporation Tapered roller bearing
CN106917817A (en) * 2015-12-17 2017-07-04 株式会社捷太格特 Taper roll bearing
CN106917817B (en) * 2015-12-17 2020-06-09 株式会社捷太格特 Tapered roller bearing

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