JP5005207B2 - Tapered roller bearing - Google Patents

Tapered roller bearing Download PDF

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JP5005207B2
JP5005207B2 JP2005311654A JP2005311654A JP5005207B2 JP 5005207 B2 JP5005207 B2 JP 5005207B2 JP 2005311654 A JP2005311654 A JP 2005311654A JP 2005311654 A JP2005311654 A JP 2005311654A JP 5005207 B2 JP5005207 B2 JP 5005207B2
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tapered
tapered roller
cage
outer ring
roller bearing
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JP2007120576A (en
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崇 辻本
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NTN Corp
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NTN Corp
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Priority to PCT/JP2006/320095 priority patent/WO2007049450A1/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
    • 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
    • F16C33/56—Selection of substances
    • F16C33/565—Coatings
    • 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
    • F16C33/4617—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
    • F16C33/467—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
    • 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
    • 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
    • F16C33/66—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
    • 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
    • F16H—GEARING
    • F16H48/00—Differential gearings
    • F16H48/38—Constructional details
    • F16H48/42—Constructional details characterised by features of the input shafts, e.g. mounting of drive gears thereon
    • F16H2048/423—Constructional details characterised by features of the input shafts, e.g. mounting of drive gears thereon characterised by bearing arrangement

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Rolling Contact Bearings (AREA)
  • General Details Of Gearings (AREA)

Description

この発明は円すいころ軸受に関し、たとえば自走車両のデファレンシャルやトランスミッション等の動力伝達軸を支持する軸受に適用することができる。   The present invention relates to a tapered roller bearing and can be applied to a bearing that supports a power transmission shaft such as a differential of a self-propelled vehicle or a transmission.

図７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との間に円すいころ軸受 ４３が介装される。この例では、メインドライブギヤ４２の内周に円すいころ軸受 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、円すいころ軸受 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. 7 shows an example of the configuration of a vehicle 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 directly formed 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.

図８は、自動車のデファレンシャルの構成を例示したものである。このデファレンシャルは、プロペラシャフト（図示省略）に連結され、デファレンシャルケース２１内に挿入したドライブピニオン２２が差動歯車ケース２３に取り付けたリングギヤ２４とかみ合い、差動歯車ケース２３の内部に取り付けたピニオンギヤ２５が、差動歯車ケース２３に左右から挿入されるドライブシャフト（図示省略）と結合するサイドギヤ２６とかみ合って、エンジンの駆動力をプロペラシャフトから左右のドライブシャフトに伝達するようになっている。このデファレンシャルでは、動力伝達軸であるドライブピニオン２２と差動歯車ケース２３が、それぞれ一対の円すいころ軸受１ａ，１ｂで支持してある。そして、デファレンシャルケース２１はシール部材２７ａ、２７ｂ、２７ｃで密封され、内部にており潤滑油が貯留される。各円すいころ軸受１ａ、１ｂはこの潤滑油の油浴に下部が漬かった状態で回転する。   FIG. 8 shows an example of the configuration of the automobile differential. This differential is connected to a propeller shaft (not shown), and a drive pinion 22 inserted into the differential case 21 meshes with a ring gear 24 attached to the differential gear case 23, and a pinion gear 25 attached to the inside of the differential gear case 23. However, the drive gear of the engine is transmitted from the propeller shaft to the left and right drive shafts by meshing with the side gear 26 coupled to the drive shaft (not shown) inserted into the differential gear case 23 from the left and right. In this differential, a drive pinion 22 that is a power transmission shaft and a differential gear case 23 are supported by a pair of tapered roller bearings 1a and 1b, respectively. The differential case 21 is sealed with seal members 27a, 27b, and 27c, and the lubricating oil is stored inside. Each tapered roller bearing 1a, 1b rotates with its lower part immersed in this lubricating oil bath.

前記トランスミッションやデファレンシャルに使用し得る円すいころ軸受は、円すい状の軌道面を有する外輪と、円すい状の軌道面を有し、この軌道面の小径側端部に小鍔部、大径側端部に大鍔部を有する内輪と、外輪の軌道面と内輪の軌道面との間に転動自在に配された複数の円すいころと、円すいころを円周方向等間隔に保持する保持器とを備えている。   The tapered roller bearing that can be used in the transmission and the differential has an outer ring having a conical raceway surface, a conical raceway surface, and a small flange portion and a large diameter side end portion at a small diameter side end portion of the raceway surface. An inner ring having a large collar portion, a plurality of tapered rollers arranged to roll between the raceway surface of the outer ring and the raceway surface of the inner ring, and a cage for holding the tapered rollers at equal intervals in the circumferential direction. I have.

このような円すいころ軸受では、柱部の内径面の両側に前記円すいころの外径面が摺接するテーパ面を設け、円すいころの外径面に接触疵が生じないようにしている。従来では、このテーパ面の幅方向の長さ寸法を、前記円すいころの平均直径の１１％〜２０％としている。   In such a tapered roller bearing, tapered surfaces on which the outer diameter surfaces of the tapered rollers are slidably contacted are provided on both sides of the inner diameter surface of the column portion, so that contact wrinkles are not generated on the outer diameter surface of the tapered rollers. Conventionally, the length of the tapered surface in the width direction is 11% to 20% of the average diameter of the tapered rollers.

前記したように、デファレンシャルやトランスミッションでは、円すいころ軸受はこの潤滑油の油浴に下部が漬かった状態で回転する。このように、油浴潤滑状態で使用される円すいころ軸受では、円すいころ４の外径面と保持器５の柱部内径面のテーパ面との間も、これらの面で形成されるくさび空間に入り込む潤滑油で潤滑される。   As described above, in the differential and the transmission, the tapered roller bearing rotates with the lower part immersed in the oil bath of this lubricating oil. As described above, in the tapered roller bearing used in the oil bath lubricated state, the wedge space formed by these surfaces is also formed between the outer diameter surface of the tapered roller 4 and the tapered surface of the columnar inner diameter surface of the cage 5. Lubricated with lubricating oil.

したがって、保持器のテーパ面の幅方向の長さ寸法Ｌが、円すいころの平均直径の１１％〜２０％である場合、円すいころの外径面と柱部内径面のテーパ面との間に比較的大きいくさび空間が形成され、多量の潤滑油がくさび空間に入り込む。このくさび空間からころの外径面と保持器のテーパ面との界面に入る潤滑油の量は限られているので、このように大量の潤滑油がくさび空間に入り込むと、これらの潤滑油の逃げ場がなくなって軸受回転の抵抗となり、トルク損失が大きくなる問題がある。また、このように軸受内部への流入する円すいころ軸受では、保持器の回転に対する潤滑油の流動抵抗も、無視できないトルク損失の要因となる。   Therefore, when the length dimension L in the width direction of the tapered surface of the cage is 11% to 20% of the average diameter of the tapered roller, it is between the outer diameter surface of the tapered roller and the tapered surface of the columnar inner diameter surface. A relatively large wedge space is formed, and a large amount of lubricating oil enters the wedge space. Since the amount of lubricating oil entering the interface between the outer diameter surface of the roller and the tapered surface of the cage is limited from this wedge space, if a large amount of lubricating oil enters the wedge space in this way, There is a problem that there is no escape space and there is resistance to rotation of the bearing, and torque loss increases. Further, in the tapered roller bearing that flows into the bearing as described above, the flow resistance of the lubricating oil with respect to the rotation of the cage also causes a torque loss that cannot be ignored.

そのため、軸受内部に潤滑油が流入する円すいころ軸受における潤滑油の流動抵抗によるトルク損失を低減させる必要がある。すなわち、低トルク化のために油の流動抵抗を減少させる必要がある。しかしながら、大幅な低トルク化を行うためには、転がり粘性抵抗が低下するように軸受諸元を変更することが必要である。ところが、従来の低トルク化手法（特許文献１〜３参照）では、定格荷重を低下させない低トルク化は可能であるが、軸受剛性はいくらか低下する。
特開平０９−０９６３５２号公報 特開平１１−０２１０７６５公報 特開２００３−３４３５５２号公報 特開２００３−２８１６５号公報 Therefore, it is necessary to reduce torque loss due to the flow resistance of the lubricating oil in the tapered roller bearing in which the lubricating oil flows into the bearing. That is, it is necessary to reduce the oil flow resistance in order to reduce the torque. However, in order to significantly reduce the torque, it is necessary to change the bearing specifications so that the rolling viscous resistance is reduced. However, with the conventional torque reduction technique (see Patent Documents 1 to 3), it is possible to reduce the torque without reducing the rated load, but the bearing rigidity is somewhat reduced.
JP 09-096352 A Japanese Patent Laid-Open No. 11-0210765 JP 2003-343552 A JP 2003-28165 A

一方、自動車のトランスミッションには、近年、ミッションのＡＴ・ＣＶＴ化、低燃費化などのため、低粘度オイルが使用される傾向にあるが、低粘度オイルが使用される環境下では、油温が高い、油量が少ない、予圧抜けが発生する等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での表面起点剥離が、面圧の高い内輪の軌道面に生じることがある。   On the other hand, low-viscosity oil tends to be used for automobile transmissions in recent years for the purpose of AT / CVT missions, fuel efficiency reduction, etc., but in environments where low-viscosity oil is used, the oil temperature is low. When unfavorable conditions such as high, low oil volume, preload loss occur, etc., surface origin separation due to poor lubrication may occur on the raceway surface of the inner ring 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９に記載の円錐ころ軸受がある（特許文献４参照）。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１０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。   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. 9 (see Patent Document 4). 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. 10, the retainer 62 has a small-diameter-side annular portion 62a, a large-diameter-side annular portion 62b, and 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 parts 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.

特許文献４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 4, 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.

この発明の目的は、ころ本数を増やすことによって負荷容量の増加と軌道面の面圧過大による早期破損を防止し、かつ軸受剛性を低下させることなく、低トルク化を実現することができて、引きずりトルクの発生を抑制することができる円すいころ軸受を提供することにある。   The object of the present invention is to increase the number of rollers to prevent an early breakage due to an increase in load capacity and excessive surface pressure of the raceway surface, and to realize a reduction in torque without reducing bearing rigidity. An object of the present invention is to provide a tapered roller bearing capable of suppressing the generation of drag torque.

本発明の円すいころ軸受は、内輪と、外輪と、内輪と外輪との間に転動自在に配された複数の円すいころと、円すいころを円周所定間隔に保持するポケットを有する保持器とを備え、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円すいころ軸受において、前記保持器は外輪の内径面に接近して配設されるとともに、前記保持器の突起部が、ポケット間に形成される柱部の外径面の周方向中央部に設けられ、かつ、前記柱部の内径面の両側に、前記円すいころの外径面が摺接し、柱部の外径面に達しないテーパ面を設けるとともに、潤滑油の逃げ場確保のために、このテーパ面の幅方向の長さ寸法を、前記円すいころの平均直径の５％以上で、１１％未満とし、さらに潤滑油の流動抵抗減少化のために、前記柱部の厚さ寸法を、前記円すいころの平均直径の５％以上で、１７％未満としたものである。 A tapered roller bearing according to the present invention includes 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 having a pocket for holding the tapered rollers at a predetermined circumferential interval. A cone formed on the outer diameter surface of the cage with a convex shape toward the inner diameter surface of the outer ring and forming a plurality of projections at predetermined intervals around the inner diameter surface of the outer ring. In the roller bearing, the cage is disposed close to the inner diameter surface of the outer ring, and the protrusion of the cage is provided at the center in the circumferential direction of the outer diameter surface of the column portion formed between the pockets. and, on both sides of the inner surface of the pillar portion, and the outer diameter surface is in sliding contact before Symbol tapered rollers, provided with a tapered surface does not reach the outer diameter surface of the pillar portion, for escape securing the lubricating oil, The length dimension in the width direction of the tapered surface is 5% or more of the average diameter of the tapered rollers. , And less than 11%, more for flow resistance reduction of the lubricating oil, the thickness of the pillar portion, at least 5% of the average diameter of the tapered rollers is obtained by less than 17%.

テーパ面の幅方向の長さ寸法を、円すいころの平均直径の１１％未満（好ましくは９％以下）としたことにより、円すいころの外径面とテーパ面との間にあまり大きなくさび空間が形成されない。テーパ面の幅方向の長さ寸法が、円すいころの平均直径の５％未満では、円すいころの外径面とテーパ面との弾性接触領域がテーパ面の幅よりも大きくなるおそれがあるので、テーパ面の幅方向の長さ寸法を、円すいころの平均直径の５％以上とするのが好ましい。   By making the length dimension of the tapered surface in the width direction less than 11% (preferably 9% or less) of the average diameter of the tapered roller, a very large wedge space is formed between the outer diameter surface of the tapered roller and the tapered surface. Not formed. If the length dimension in the width direction of the tapered surface is less than 5% of the average diameter of the tapered roller, the elastic contact area between the outer diameter surface of the tapered roller and the tapered surface may be larger than the width of the tapered surface. The length dimension of the tapered surface in the width direction is preferably 5% or more of the average diameter of the tapered rollers.

前記突起部を形成することにより円すい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。また、保持器の接触による引きずりトルクを発生させないため、保持器ポケット部の摩耗も最小限とすることができる。   By forming the protrusion, a minute gap between the retainer 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. Further, since the drag torque due to the contact of the cage is not generated, the wear of the cage pocket portion can be minimized.

前記柱部の厚さ寸法を、前記円すいころの平均直径の５％以上で、１７％未満とすることにより、柱部の厚みを薄くして、保持器の回転に対する潤滑油の流動抵抗を小さくすることができる。なお、柱部の厚さ寸法を円すいころの平均直径の５％未満では、保持器の剛性を十分に確保できないので、柱部の厚さ寸法を円すいころの平均直径の５％以上とするのが好ましい。 The thickness of the pillar portion, at least 5% of the average diameter of the tapered rollers, by less than 17%, by reducing the thickness of the column part, reduce the flow resistance of the lubricating oil to the rotation of the cage can do. If the thickness dimension of the column part is less than 5% of the average diameter of the tapered roller, the rigidity of the cage cannot be sufficiently secured. Therefore, the thickness dimension of the column part is set to 5% or more of the average diameter of the tapered roller. Is preferred.

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。これにより、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。   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. It was 50% or more of the dimension. As a result, a good wedge-shaped oil film is formed between the inner ring surface of the outer ring and the outer ring is kept out of contact with the dynamic pressure of the wedge-shaped oil film when the bearing rotates.

上述した各円すいころ軸受は、自走車両の動力伝達軸を支持するものに好適である。   Each tapered roller bearing described above is suitable for supporting a power transmission shaft of a self-propelled vehicle.

本発明の円すいころ軸受は、テーパ面の幅方向の長さ寸法を、円すいころの平均直径の５％以上で、１１％未満（好ましくは９％以下）としたので、円すいころの外径面とテーパ面との間にあまり大きなくさび空間が形成されない。このため、くさび空間に入り込む潤滑油の量を少なくし、潤滑油の逃げ場が無くなることによるトルク損失を低減できる。   In the tapered roller bearing of the present invention, the length dimension in the width direction of the tapered surface is 5% or more and less than 11% (preferably 9% or less) of the average diameter of the tapered roller. A very large wedge space is not formed between the taper surface and the taper surface. For this reason, the amount of lubricating oil entering the wedge space can be reduced, and torque loss due to the absence of the escape space for the lubricating oil can be reduced.

円すい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。   A plurality of protrusions that protrude toward the inner peripheral surface of the outer ring are formed on the outer peripheral surface of the cage of the tapered roller bearing at predetermined intervals around the outer ring, so that the roller outer diameter surface is brought close to the inner diameter surface of the outer ring. Even if the number is increased, 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.

ところで、図１２は円すいころ軸受において円すいころピッチ径（ＰＣＤ）を変化させたときの剛性比（−●−）およびトルク比（−○−）を表したものである。図１２に示すように、ＰＣＤを小さくすると軸受のトルクは大幅に低下するが、軸受剛性はあまり低下しないことが、円すいころの弾性変形量を計算確認した結果として得られた。そこで、ころ本数を減らさないか増加させつつ、ＰＣＤを小さくすることによって、剛性を低下させずにトルクを低減させることができる。   FIG. 12 shows the rigidity ratio (− ● −) and torque ratio (− ◯ −) when the tapered roller pitch diameter (PCD) is changed in the tapered roller bearing. As shown in FIG. 12, when the PCD is reduced, the bearing torque is greatly reduced, but the bearing rigidity is not reduced so much as a result of calculating and confirming the amount of elastic deformation of the tapered roller. Therefore, the torque can be reduced without reducing the rigidity by reducing the PCD while decreasing or increasing the number of rollers.

本発明では、円すい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することによって、ころ本数を増大させつつころＰＣＤを小さくできるようにした。このため、軸受剛性を低下させることなく、低トルク化を実現できる。また、ころ本数を増加させることによって、負荷容量がアップするばかりでなく、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, the roller PCD is made small while increasing the number of rollers by forming a plurality of protrusions that are convex toward the inner peripheral surface of the outer ring on the outer peripheral surface of the retainer of the tapered roller bearing at predetermined circumferential intervals. I was able to do it. For this reason, a reduction in torque can be realized without reducing the bearing rigidity. Also, by increasing the number of rollers, not only the load capacity is increased, but the maximum surface pressure of the inner and outer ring raceway surfaces can be reduced by increasing the number of rollers without impairing the torque characteristics of the bearing. Even when adverse conditions such as a small amount of oil and occurrence of preload loss result in severe lubrication conditions, it is possible to prevent surface-origin separation having an extremely short life, particularly on the inner ring raceway surface.

また、柱部の厚さ寸法を、円すいころの平均直径の５％以上で、１７％未満とすることにより、柱部の厚みを薄くして、保持器の回転に対する潤滑油の流動抵抗を小さくし、トルク損失をより低減できる。   In addition, by setting the thickness of the column portion to 5% or more and less than 17% of the average diameter of the tapered rollers, the thickness of the column portion is reduced, and the flow resistance of the lubricating oil to the rotation of the cage is reduced. Thus, torque loss can be further reduced.

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。このため、トルク損失や保持器ないし外輪軌道面の損傷を安定して防止することができる。   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. For this reason, it is possible to stably prevent torque loss and damage to the cage or the outer ring raceway surface.

以下、図面に従ってこの発明の実施の形態を説明する。   Embodiments of the present invention will be described below with reference to the drawings.

図１および図４に示すように、この実施の形態の円すいころ軸受１は、内輪２と、外輪３と、円すいころ４と、保持器５とで構成されている。内輪２は外周に円すい状の軌道面２ａを有し、外輪３は内周に円すい状の軌道面３ａを有する。複数の円すいころ４が、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介在させてある。円すいころ４は保持器５に形成されたポケット５ｄ内に収容されている。各円すいころ４は、内輪２の軌道面２ａの両側に設けた小つば２ｂと大つば２ｃとで軸方向への移動を規制されている。 As shown in FIGS. 1 and 4, the tapered roller bearing 1 of this embodiment includes an inner ring 2, an outer ring 3, a tapered roller 4, and a cage 5. The inner ring 2 has a conical track surface 2a on the outer periphery, and the outer ring 3 has a conical track surface 3a on the inner periphery. A plurality of tapered rollers 4 are interposed between the raceway surface 2a of the inner ring 2 and the raceway surface 3a of the outer ring 3 so as to be freely rollable. The tapered roller 4 is accommodated in a pocket 5d formed in the cage 5. Each tapered roller 4 is restricted from moving in the axial direction by a small brim 2 b and a large brim 2 c provided on both sides of the raceway surface 2 a of the inner ring 2.

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（小径リング部）５ａと、大径側環状部（大径リング部）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、円すいころ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 (small-diameter ring portion) 5a and a large-diameter side annular portion. (Large-diameter ring portion) 5b, a plurality of column portions 5c that connect the small-diameter side annular portion 5a and the large-diameter side annular portion 5b in the axial direction, and a tapered roller provided between the column portions 5c adjacent in the circumferential direction. And a plurality of pockets 5d for accommodating 4 in a rollable manner. 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）。５０％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 50%, 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、円すいころ軸受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、円すいころ軸受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。すなわち、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。 The surface of the cage 5, particularly the outer diameter surface of the cage 5, should be as smooth as possible. That is, during the rotation of the tapered roller bearing 1, a wedge-like 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 if severe lubrication conditions occur before the wedge roller oil film is formed due to the low rotational speed immediately after the tapered roller bearing 1 rotates, the outer diameter surface or protrusion of the cage 5 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. That is, by performing such a smoothing process, it is possible to reduce torque loss and cage wear at the start of the bearing.

保持器５は鋼板プレス製品のほか、樹脂製の保持器１５（図５参照）としてもよい。この樹脂製保持器１５の柱部１５ｃ外径面にも、鋼板プレス製保持器５と同様に突起部１５ｆ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１５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、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。また、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利点がある。なお、図５に示す円すいころ軸受において、図１に示す円すいころ軸受と同一構成については図１と同一符号を付してその説明を省略する。図５において、１５ｄはポケットを示し、１５ｅは鍔部を示している。   The cage 5 may be a resin-made cage 15 (see FIG. 5) in addition to a steel plate press product. Similarly to the retainer 5 made of a steel plate press, a protrusion 15 f is integrally formed on the outer diameter surface of the column portion 15 c of the resin retainer 15. 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. Since the resin cage 15 has a feature that the weight is lighter and the friction coefficient is smaller than the steel plate press cage 5, 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 when starting the bearing. Further, the steel plate press cage is advantageous in that it is suitable for extending the bearing life because it has high rigidity and wear resistance. In the tapered roller bearing shown in FIG. 5, the same components as those of the tapered roller bearing shown in FIG. In FIG. 5, 15d indicates a pocket, and 15e indicates a buttocks.

本発明の円すいころ軸受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（１５）が回転し始めると、外輪軌道面と保持器５（１５）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（１５）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 (15) begins to rotate, the outer ring raceway surface and the protrusion 5f of the cage 5 (15). A wedge-shaped oil film is formed between the two. 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 cage 5 (15) is increased and brought close to the outer ring raceway surface, the bearing 1 becomes large. It is possible to rotate without causing wear or torque loss, and it is possible to increase the number of rollers without difficulty.

保持器５は、図６（Ｂ）に示すように、柱部５ｃの内径面の両側には、円すいころ４の外径面が摺接するテーパ面１８が設けられ、このテーパ面１８の幅方向の長さ寸法Ｌは、円すいころ４の平均直径Ｄの５％以上で、１１％未満（好ましくは９％以下）とされる。テーパ面１８の幅方向の長さ寸法Ｌを、円すいころ４の平均直径の１１％未満としたことにより、円すいころ４の外径面とテーパ面１８との間にあまり大きなくさび空間が形成されない。テーパ面１８の幅方向の長さ寸法Ｌが、円すいころの平均直径の５％未満では、円すいころ４の外径面とテーパ面１８との弾性接触領域がテーパ面１８の幅よりも大きくなるおそれがあるので、テーパ面１８の幅方向の長さ寸法Ｌを、円すいころ４の平均直径の５％以上とするのが好ましい。なお、この実施形態では、テーパ面１８の幅方向の長さ寸法Ｌを、円すいころ４の平均直径Ｄの７％とした。また、図６においては、図面の簡略化のために、突起部５ｆの図示を省略しているが、実際には突起部５ｆが設けられている。なお、テーパ面１８は図６（Ｂ）に示すように柱部５ｃの外径面に達しないように設定している。 As shown in FIG. 6B, the retainer 5 is provided with tapered surfaces 18 on both sides of the inner diameter surface of the column portion 5c so that the outer diameter surfaces of the tapered rollers 4 are in sliding contact with each other. The length dimension L is 5% or more of the average diameter D of the tapered rollers 4 and less than 11% (preferably 9% or less). By setting the length dimension L in the width direction of the tapered surface 18 to less than 11% of the average diameter of the tapered roller 4, a very large wedge space is not formed between the outer diameter surface of the tapered roller 4 and the tapered surface 18. . When the length dimension L in the width direction of the tapered surface 18 is less than 5% of the average diameter of the tapered roller, the elastic contact region between the outer diameter surface of the tapered roller 4 and the tapered surface 18 becomes larger than the width of the tapered surface 18. Therefore, it is preferable that the length L in the width direction of the tapered surface 18 is 5% or more of the average diameter of the tapered rollers 4. In this embodiment, the length dimension L in the width direction of the tapered surface 18 is 7% of the average diameter D of the tapered rollers 4. Further, in FIG. 6, for the sake of simplification of the drawing, the illustration of the protrusion 5 f is omitted, but the protrusion 5 f is actually provided. The tapered surface 18 is set so as not to reach the outer diameter surface of the column portion 5c as shown in FIG.

また、柱部５ｃの厚さ寸法Ｔを、円すいころ４の平均直径Ｄの５％以上で、１７％未満とする。これにより、保持器５の回転に対する潤滑油の流動抵抗を小さくできるようにしている。なお、柱部５ｃの厚さ寸法Ｔを円すいころの平均直径の５％未満では、保持器５の剛性を十分に確保できないので、柱部５ｃの厚さ寸法Ｔを円すいころ４の平均直径の５％以上とするのが好ましい。この実施形態では、柱部５ｃの厚さ寸法Ｔを、円すいころ４の平均直径Ｄの１０％とした。なお、柱部５ｃの厚さ寸法Ｔは、突起部５ｆを含み厚さである。   Further, the thickness dimension T of the column part 5c is set to 5% or more and less than 17% of the average diameter D of the tapered rollers 4. Thereby, the flow resistance of the lubricating oil with respect to the rotation of the cage 5 can be reduced. In addition, if the thickness dimension T of the column part 5c is less than 5% of the average diameter of the tapered roller, the rigidity of the cage 5 cannot be sufficiently secured. Therefore, the thickness dimension T of the column part 5c is equal to the average diameter of the tapered roller 4. 5% or more is preferable. In this embodiment, the thickness dimension T of the column part 5 c is 10% of the average diameter D of the tapered rollers 4. In addition, the thickness dimension T of the column part 5c is thickness including the protrusion part 5f.

本発明の円すいころ軸受は、テーパ面１８の幅方向の長さ寸法Ｌを、円すいころ４の平均直径Ｄの５％以上で、１１％未満（好ましくは９％以下）としたので、円すいころ４の外径面とテーパ面１８との間にあまり大きなくさび空間が形成されない。このため、くさび空間に入り込む潤滑油の量を少なくし、潤滑油の逃げ場が無くなることによるトルク損失を低減できる。   In the tapered roller bearing of the present invention, the length dimension L in the width direction of the tapered surface 18 is 5% or more of the average diameter D of the tapered roller 4 and less than 11% (preferably 9% or less). No large wedge space is formed between the outer diameter surface 4 and the tapered surface 18. For this reason, the amount of lubricating oil entering the wedge space can be reduced, and torque loss due to the absence of the escape space for the lubricating oil can be reduced.

円すいころ軸受の保持器５の外周面に外輪の内周面に向かって凸状をなす突起部５ｆ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５ｆ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。   Since a plurality of protrusions 5f that are convex toward the inner peripheral surface of the outer ring are formed at predetermined intervals on the outer peripheral surface of the retainer 5 of the tapered roller bearing, the outer diameter surface of the cage is brought close to the inner diameter surface of the outer ring. Even if the number of rollers accommodated is increased, a good lubricating action by the wedge-shaped oil film can be obtained between the protrusion 5f and the inner peripheral surface of the outer ring.

円すいころ軸受の保持器５の外周面に外輪３の内周面に向かって凸状をなす突起部５ｆを円周所定間隔で複数形成することによって、ころ本数を増大させつつころＰＣＤを小さくできるようにした。このため、軸受剛性を低下させることなく、低トルク化を実現できる。また、ころ本数を増加させることによって、負荷容量がアップするばかりでなく、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。さらに、保持器５の接触による引きずりトルクの発生を抑制することができ、保持器ポケット５ｄの摩耗も最小限とすることができる。   By forming a plurality of protruding portions 5f that protrude toward the inner peripheral surface of the outer ring 3 on the outer peripheral surface of the retainer 5 of the tapered roller bearing at predetermined circumferential intervals, the roller PCD can be reduced while increasing the number of rollers. I did it. For this reason, a reduction in torque can be realized without reducing the bearing rigidity. Also, by increasing the number of rollers, not only the load capacity is increased, but the maximum surface pressure of the inner and outer ring raceway surfaces can be reduced by increasing the number of rollers without impairing the torque characteristics of the bearing. Even when adverse conditions such as a small amount of oil and occurrence of preload loss result in severe lubrication conditions, it is possible to prevent surface-origin separation having an extremely short life, particularly on the inner ring raceway surface. Further, the generation of drag torque due to the contact of the cage 5 can be suppressed, and wear of the cage pocket 5d can be minimized.

また、柱部５ｃの厚さ寸法Ｔを、円すいころの平均直径の５％以上で、１７％未満とすることにより、柱部５ｃの厚みを薄くして、保持器５の回転に対する潤滑油の流動抵抗を小さくし、トルク損失をより低減できる。   Moreover, the thickness dimension T of the column part 5c is 5% or more and less than 17% of the average diameter of the tapered rollers, so that the thickness of the column part 5c is reduced and the lubricating oil against rotation of the cage 5 is reduced. The flow resistance can be reduced, and torque loss can be further reduced.

突起部５ｆ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５ｆの幅寸法を保持器５の柱部５ｃ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５ｆと外輪３との非接触状態が維持される。このため、トルク損失や保持器ないし外輪軌道面の損傷を安定して防止することができる。   The shape of the protrusion 5f is an arc of a cross section with a radius of curvature smaller than the radius of the outer ring raceway surface, and the width of the protrusion 5f is 50% or more of the width of the pillar 5c of the cage 5, thereby A good wedge-shaped oil film is formed between the outer ring inner diameter surface and the non-contact state between the cage 5f and the outer ring 3 by the dynamic pressure of the wedge-shaped oil film during rotation. For this reason, it is possible to stably prevent torque loss and damage to the cage or the outer ring raceway surface.

以上、本発明の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（１５ｆ）を柱部５ｃ（１５ｃ）の外径面に形成したが、これに加えて、保持器５（１５）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 the embodiments of the present invention have been described above, the present invention is not limited to the above embodiments and can be variously modified. For example, in the above-described embodiment, the protruding portion 5f (15f) is formed on the outer diameter surface of the column portion 5c (15c), but in addition to this, the small-diameter side annular portion 5a and the large-diameter side annular portion of the cage 5 (15). It can also be formed on the outer diameter surface of 5b.

また、本発明に係る円すいころ軸受１ は、自動車のトランスミッションやデファレンシャルに使用することができるが、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 automobile transmissions and differentials, but it can also be used for applications other than automobile gear devices.

図６（Ａ）（Ｂ）に示した、テーパ面の長さ寸法Ｌを円すいころの平均直径Ｄの７％とした保持器を用いた円すいころ軸受（実施例）と、テーパ面の長さ寸法Ｌを円すいころの平均直径Ｄの１３％とした従来の保持器を用いた円すいころ軸受（比較例）とを用意した。なお、各円すいころ軸受は、寸法が外径１００ｍｍ、内径４５ｍｍ、幅２７．２５ｍｍとした。また、保持器の柱部の厚さ寸法Ｔは、実施例のものが円すいころの平均直径Ｄの１３％、比較例のものが１７％とした。   6A and 6B, a tapered roller bearing (Example) using a cage in which the length L of the tapered surface is 7% of the average diameter D of the tapered roller, and the length of the tapered surface. A tapered roller bearing (comparative example) using a conventional cage having a dimension L of 13% of the average diameter D of the tapered roller was prepared. Each tapered roller bearing had an outer diameter of 100 mm, an inner diameter of 45 mm, and a width of 27.25 mm. Further, the thickness T of the column portion of the cage was set to 13% of the average diameter D of the tapered roller in the example and 17% in the comparative example.

実施例と比較例の円すいころ軸受について、縦型トルク試験機を用いたトルク測定試験を行った。試験条件は以下のとおりである。
アキシアル荷重：３００ｋｇｆ
回転速度：３００〜２０００ｒｐｍ（１００ｒｐｍピッチ）
潤滑条件：油浴潤滑（潤滑油：７５Ｗ−９０） About the tapered roller bearing of an Example and a comparative example, the torque measurement test using the vertical torque tester was done. The test conditions are as follows.
Axial load: 300kgf
Rotational speed: 300-2000 rpm (100 rpm pitch)
Lubrication condition: oil bath lubrication (lubricating oil: 75W-90)

図１１は、上記トルク測定試験の結果を示す。図１１のグラフの縦軸は、比較例のもののトルクに対する実施例のもののトルクの低減率を表す。テーパ面の長さ寸法Ｌを円すいころの平均直径Ｄの７％と小さくした実施例のものは、低速回転から高速回転まで顕著なトルク低減効果が認められ、試験の最高回転速度である２０００ｒｐｍでも１２．０％のトルク低減率が得られている。この実施例のトルク低減効果には、柱部の厚さ寸法Ｔを薄くして、保持器の回転に対する潤滑油の流動抵抗を小さくした効果も含まれている。   FIG. 11 shows the results of the torque measurement test. The vertical axis of the graph in FIG. 11 represents the torque reduction rate of the embodiment with respect to the torque of the comparative example. In the example in which the length L of the tapered surface is as small as 7% of the average diameter D of the tapered roller, a remarkable torque reduction effect is recognized from low speed rotation to high speed rotation, and even at the maximum rotation speed of 2000 rpm of the test. A torque reduction rate of 12.0% is obtained. The torque reduction effect of this embodiment includes the effect of reducing the flow resistance of the lubricating oil against the rotation of the cage by reducing the thickness dimension T of the column portion.

本発明に係る円錐ころ軸受の部分断面図である。It is a fragmentary sectional view of the tapered roller bearing which concerns on this invention. 保持器の柱部の断面図である。It is sectional drawing of the pillar part of a holder | retainer. 保持器の部分斜視図である。It is a 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であり、（Ｂ）は（Ａ）のＢ−Ｂ線矢視断面図である。(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であり、（Ｂ）は（Ａ）のＢ−Ｂ線矢視断面図である。(A) is a longitudinal cross-sectional view of the tapered roller bearing using the resin cage, and (B) is a cross-sectional view taken along the line BB of (A). 図１の保持器を示し、（Ａ）は展開平面図であり、（Ｂ）は（Ａ）のＸ−Ｘ線断面図である。1 shows the cage of FIG. 1, (A) is a developed plan view, and (B) is a sectional view taken along line XX of (A). FIG. 自動車のトランスミッションの部分断面図である。It is a fragmentary sectional view of the transmission of a car. 自動車のデファレンシャルを示す断面図である。It is sectional drawing which shows the differential of a motor vehicle. 従来の円錐ころ軸受の部分断面図である。It is a 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である。It is a perspective view of the retainer of the conventional tapered roller bearing. トルク測定試験の結果を示すグラフである。It is a graph which shows the result of a torque measurement test. 円すいころ軸受において円すいころピッチ径（ＰＣＤ）を変化させたときの剛性比およびトルク比の変化を表す線図である。It is a diagram showing the change of a rigidity ratio and a torque ratio when changing a tapered roller pitch diameter (PCD) in a tapered roller bearing.

符号の説明Explanation of symbols

２ 内輪
２ａ 軌道面
３ 外輪
３ａ 軌道面
５、１５ 保持器
５ａ、１５ａ 小径リング部（小径側環状部）
５ｂ、１５ｂ 大径リング部（大径側環状部）
５ｃ、１５ｃ 柱部
５ｄ ポケット
５ｆ、１５ｆ 突起部
５ｅ、１５ｅ 鍔部
１８ テーパ面


2 Inner ring 2a Raceway surface 3 Outer ring 3a Raceway surface 5, 15 Cage 5a, 15a Small diameter ring part (small diameter side annular part)
5b, 15b Large-diameter ring part (large-diameter side annular part)
5c, 15c Pillar part 5d Pocket 5f, 15f Protrusion part 5e, 15e ridge part 18 taper surface


Claims (3)

内輪と、外輪と、内輪と外輪との間に転動自在に配された複数の円すいころと、円すいころを円周所定間隔に保持するポケットを有する保持器とを備え、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円すいころ軸受において、
前記保持器は外輪の内径面に接近して配設されるとともに、前記保持器の突起部が、ポケット間に形成される柱部の外径面の周方向中央部に設けられ、かつ、前記柱部の内径面の両側に、前記円すいころの外径面が摺接し、柱部の外径面に達しないテーパ面を設けるとともに、潤滑油の逃げ場確保のために、このテーパ面の幅方向の長さ寸法を、前記円すいころの平均直径の５％以上で、１１％未満とし、さらに潤滑油の流動抵抗減少化のために、前記柱部の厚さ寸法を、前記円すいころの平均直径の５％以上で、１７％未満としたことを特徴とする円すいころ軸受。 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 having a pocket for holding the tapered rollers at a predetermined circumferential interval. In the tapered roller bearing in which a plurality of protrusions forming a minute gap between the inner surface of the outer ring and the inner surface of the outer ring are formed at predetermined intervals on the radial surface.
The retainer is disposed close to the inner diameter surface of the outer ring, and the protrusion of the retainer is provided at the center in the circumferential direction of the outer diameter surface of the column portion formed between the pockets, and on both sides of the inner surface of the pillar portion, and the outer diameter surface is in sliding contact before Symbol tapered rollers, provided with a tapered surface does not reach the outer diameter surface of the pillar portion, for escape securing the lubricating oil, of the tapered surface The length dimension in the width direction is set to 5% or more and less than 11% of the average diameter of the tapered roller, and the thickness dimension of the column portion is set to be equal to that of the tapered roller in order to reduce the flow resistance of the lubricating oil . Tapered roller bearings characterized in that the average diameter is 5% or more and less than 17%. 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に記載の円すいころ軸受。   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 a dimension. 自走車両の動力伝達軸を支持することを特徴とする請求項１又は請求項２に記載の円すいころ軸受。   The tapered roller bearing according to claim 1 or 2, wherein a power transmission shaft of the self-propelled vehicle is supported.
JP2005311654A 2005-10-26 2005-10-26 Tapered roller bearing Expired - Fee Related JP5005207B2 (en)

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JP2005311654A JP5005207B2 (en) 2005-10-26 2005-10-26 Tapered roller bearing
PCT/JP2006/320095 WO2007049450A1 (en) 2005-10-26 2006-10-06 Tapered roller bearing

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DE102007044901B4 (en) * 2007-09-19 2016-02-25 Ab Skf Cylindrical roller bearing cage and roller bearing
DE202008014280U1 (en) * 2008-10-27 2010-04-08 Ab Skf Rolling bearing cage
CN102767611A (en) * 2012-07-28 2012-11-07 西安煤矿机械有限公司 Method for adjusting clearance of bearing at upper part of heavy loaded planetary reducer of coal cutter cutting unit
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JP2005147364A (en) * 2003-11-19 2005-06-09 Nakanishi Metal Works Co Ltd Holder for roller bearings, and its manufacturing method
JP2005147365A (en) * 2003-11-19 2005-06-09 Nakanishi Metal Works Co Ltd Retainer for conical roller bearing and assembling method of conical roller bearing
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