JP4151347B2 - Tapered roller bearing - Google Patents

Tapered roller bearing Download PDF

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Publication number
JP4151347B2
JP4151347B2 JP2002233777A JP2002233777A JP4151347B2 JP 4151347 B2 JP4151347 B2 JP 4151347B2 JP 2002233777 A JP2002233777 A JP 2002233777A JP 2002233777 A JP2002233777 A JP 2002233777A JP 4151347 B2 JP4151347 B2 JP 4151347B2
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Japan
Prior art keywords
tapered roller
small
diameter side
inner ring
sectional area
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Expired - Fee Related
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Japanese (ja)
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JP2004076766A (en
Inventor
博文 百々路
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JTEKT Corp
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JTEKT Corp
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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
    • F16C33/66—Special parts or details in view of lubrication
    • F16C33/6637—Special parts or details in view of lubrication with liquid lubricant
    • F16C33/6659—Details of supply of the liquid to the bearing, e.g. passages or nozzles
    • F16C33/667—Details of supply of the liquid to the bearing, e.g. passages or nozzles related to conditioning, e.g. cooling, filtering
    • 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
    • F16C33/54—Cages for rollers or needles made from wire, strips, or sheet metal
    • 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
    • F16C33/6659—Details of supply of the liquid to the bearing, e.g. passages or nozzles
    • F16C33/6674—Details of supply of the liquid to the bearing, e.g. passages or nozzles related to the amount supplied, e.g. gaps to restrict flow of the liquid
    • 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
    • F16C2300/00—Application independent of particular apparatuses
    • F16C2300/02—General use or purpose, i.e. no use, purpose, special adaptation or modification indicated or a wide variety of uses mentioned

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

Description

【０００１】
【発明の属する技術分野】
本発明は、高速回転で使用される油潤滑方式の円すいころ軸受に関する。
【０００２】
【従来の技術】
従来より、内輪と外輪の間に、保持器によって回動自在に保持された複数の円すいころを介装させることにより、軸を中心に内輪と外輪を相対回転させる円すいころ軸受がある。
【０００３】
円すいころ軸受では、各部における摩擦や焼付きを防止するため、十分に潤滑することが重要となる。特に、高速回転で使用される場合には、潤滑性に優れた油潤滑方式が採用されている。
【０００４】
【発明が解決しようとする課題】
油潤滑方式の円すいころ軸受の場合、回転時に潤滑油が、円すいころの小径側の軸受端部から円すいころの大径側の軸受端部へ流れる。
【０００５】
軸受中を潤滑油が流れる際に、潤滑油が円すいころの転動によって攪拌される。軸受内部に滞留する潤滑油の量が多くなると、攪拌抵抗が増大し、軸受の損失トルクも大きくなる。
【０００６】
【課題を解決するための手段】
本発明の円すいころ軸受は、内輪と、外輪と、前記内輪と前記外輪の間に保持器によって回動自在に保持された複数の円すいころとを含み、前記内輪は、前記円すいころの小径側における軸方向端縁において径方向外向きに突出させた小鍔部を有し、前記保持器は、各円すいころを収納するポケットを有した環状板部と、前記円すいころの小径側の端縁において前記環状板部を径方向内向きに折曲してなるフランジ部とを有し、前記フランジ部の内径側先端と前記内輪の小鍔部の外周面とが互いの間に隙間を介して対面しており、前記外輪の小径側における軸方向端部と前記内輪の小鍔部との間における前記保持器を除いた断面積に相当する潤滑油流路断面積Ａ1、前記円すいころの小径側端面における前記外輪と前記内輪間における前記保持器と前記円すいころおよび前記小鍔部の投影面積を除いた断面積に相当する潤滑油流路断面積Ａ2、前記外輪の大径側における軸方向端部と前記内輪の大鍔部との間における前記保持器と前記円すいころを除いた断面積に相当する潤滑油流路断面積Ａ3が、Ａ1≦Ａ2＜Ａ3の関係を満たすものである。
【０００７】
本発明の円すいころ軸受によると、潤滑油が軸受に入る入口側の潤滑油流路断面積Ａ1，Ａ2は、潤滑油が軸受から出る出口側の潤滑油流路断面積Ａ3より小さくなっている。よって、軸受に入る潤滑油の油量が軸受から出る潤滑油の油量より少なくなり、軸受内部に滞留する潤滑油の量が少なくなる。その結果、円すいころの転動によって攪拌される潤滑油の量が少なくなり、軸受の損失トルクが小さくなる。
【０００８】
【発明の実施の形態】
以下、本発明の一実施の形態を図１ないし図５を用いて説明する。
【０００９】
図１は円すいころ軸受の部分縦断面図、図２は円すいころ軸受のＬ1部分の断面図、図３は円すいころ軸受のＬ2部分の断面図、図４は円すいころ軸受のＬ3部分の断面図、図５は円すいころ軸受の潤滑油流路断面積を示すグラフである。
【００１０】
これらの図において、１０は内輪、２０は外輪、３０は円すいころ、４０は保持器を示す。
【００１１】
内輪１０は環状に形成され、軸心Ｃに沿う方向（軸方向）の一端縁に径方向外向きに突出させた小鍔部１１を有し、他端縁には径方向外向きに突出させた大鍔部１２を有している。内輪１０の外周面（内輪軌道面）１３は、小鍔部１１から大鍔部１２にかけて外径が漸増するテーパ状に形成されている。大鍔部１２は径方向外側が厚肉となり、その軸方向内周面１２ａには円すいころ３０の大径側端面３２が接触される。
【００１２】
外輪２０は、内輪１０より大径の環状に形成され、内輪１０の内輪軌道面１３との間に円すいころ３０を保持するための間隙を介して対向配置されている。外輪２０の内周面（外輪軌道面）２１は、軸方向一端から他端にかけて内径が漸増するテーパ状に形成されている。
【００１３】
円すいころ３０は、小径側端面３１と、大径側端面３２と、テーパ状の外周面３３とを有している。円すいころ３０は、大径側端面３２の一部を内輪１０の大鍔部１２の内周面１２ａに接触させて、内輪軌道面１３ならびに外輪軌道面２１に転接される。複数の円すいころ３０が、周方向に等配されて、保持器４０にて回動自在に保持される。
【００１４】
保持器４０は、各円すいころ３０を収納するポケットを有した環状板部４１と、円すいころ３０の小径側の端縁において環状板部４１を径方向内向きに折曲してなるフランジ部４２とを有している。
【００１５】
円すいころ軸受の回転時に、潤滑油が、円すいころ３０の小径側の軸方向端部から円すいころ３０の大径側の軸方向端部へ流れる（矢印Ｑ方向）。
【００１６】
図２〜図４に、円すいころ軸受の各位置Ｌ1，Ｌ2，Ｌ3における円すいころ３０の軸心Ｍに対し直交する断面における軸受の断面図を示す。
【００１７】
図２〜図４中、点々で示した部分が、潤滑油の通る流路部となる。
【００１８】
潤滑油流路断面積Ａ1は、小鍔部１１において、内輪１０と外輪２０の間隙における保持器４０を除いた断面積に相当する。
【００１９】
潤滑油流路断面積Ａ2は、円すいころ３０の小径側において、内輪１０と外輪２０の間隙における保持器４０と円すいころ３０および小鍔部１１の投影面積を除いた断面積に相当する。すなわち、小鍔部１１が壁となり、潤滑油流路断面積Ａ2では小鍔部１１の投影面積も減じた流路面積となっている。
【００２０】
潤滑油流路断面積Ａ3は、大鍔部１２において、内輪１０と外輪２０の間隙における保持器４０と円すいころ３０を除いた断面積に相当する。
【００２１】
各位置Ｌ1，Ｌ2，Ｌ3における潤滑油流路断面積Ａ1，Ａ2，Ａ3を図５に示す。図５中、縦軸は潤滑油の流路断面積、横軸は円すいころ軸受の軸心Ｃ方向の位置を示している。
【００２２】
各位置Ｌ1，Ｌ2，Ｌ3における円すいころ軸受の潤滑油流路断面積Ａ1，Ａ2，Ａ3の関係は、下記の式（１）のようになる。
【００２３】
Ａ1≦Ａ2＜Ａ3 …（１）
式（１）に示す関係となるように、保持器４０の形状を設定したり、小鍔部１１や大鍔部１２の径方向高さを設定したり、潤滑油の入口側である円すいころの小径側における軸方向端部に遮蔽板を設置する。
【００２４】
本実施の形態では、小鍔部１１と大鍔部１２の径方向高さを調整し、保持器４０のフランジ部４２の径方向長さを調整することで、式（１）に示す関係を満たすようにする。
【００２５】
一例として、円すいころ軸受は型番３０３０６ＤＪを用い、円すいころ３０のころ数は１４個、小鍔部１１の外径はφ４１．１ｍｍ、大鍔部１２の外径はφ５４ｍｍ、保持器４０は小鍔部１１側の内径が小さくなるように屈曲させてフランジ部４２を形成し、当該フランジ部４２の内径を小鍔部１１の外径と略等しくしたものとする。
【００２６】
これにより、各潤滑油流路断面積Ａは、下記の値となる。
【００２７】
Ａ1＝２０２．５ｍｍ2
Ａ2＝２５７．３ｍｍ2
Ａ3＝３５７．３ｍｍ2
図５について、詳細に説明する。
【００２８】
図５中、点ａから点ｂに渡って流路断面積が小さくなっているのは、保持器４０のフランジ部４２によるものである。
【００２９】
点ｂから点ｃに渡って流路断面積が大きくなっているのは、小鍔部１１を乗り越えて内輪軌道面１３に達することによるものである。
【００３０】
点ｃから点ｄに渡って流路断面積が小さくなっているのは、円すいころ３０によるものである。
【００３１】
点ｄから点ｅに渡って流路断面積が大きくなっているのは、内輪軌道面１３と外輪軌道面２１の間隙が、テーパ状に広がっていることによる。
【００３２】
点ｅから点ｆに渡って流路断面積が小さくなっているのは、大鍔部１２によるものである。
【００３３】
その後、大鍔部１２を乗り越えるに伴い、流路断面積が増加する。
【００３４】
このように構成された円すいころ軸受によると、潤滑油が軸受に入る入口側の流路断面積Ａ1，Ａ2は、潤滑油が軸受から出る出口側の流路断面積Ａ3より小さくなっている。よって、軸受に入る潤滑油の油量Ｑ1が軸受から出る潤滑油の油量Ｑ2より少なくなり、軸受内部に滞留する潤滑油の量が少なくなる。その結果、円すいころ３０の転動によって攪拌される潤滑油の量が少なくなり、軸受の損失トルクが小さくなる。
【００３５】
なお、円すいころ軸受の構造は、円すいころの小径側における軸方向端部の軸受開口面積Ａ1、円すいころの小径側端面における流路断面積Ａ2、円すいころの大径側における軸方向端部の流路断面積Ａ3が、Ａ1≦Ａ2＜Ａ3の関係を満たす構造であればよい。
【００３６】
【発明の効果】
本発明の円すいころ軸受によると、撹拌トルクの低減が図れ、軸受の損失トルクが小さくなるという効果が得られる。
【図面の簡単な説明】
【図１】本発明の一実施の形態における円すいころ軸受の部分縦断面図である。
【図２】本発明の一実施の形態における円すいころ軸受のＬ1部分の断面図である。
【図３】本発明の一実施の形態における円すいころ軸受のＬ2部分の断面図である。
【図４】本発明の一実施の形態における円すいころ軸受のＬ3部分の断面図である。
【図５】本発明の一実施の形態における円すいころ軸受の潤滑油流路断面積を示すグラフである。
【符号の説明】
１０ 内輪
１１ 小鍔部
１２ 大鍔部
１３ 内輪軌道面
２０ 外輪
２１ 外輪軌道面
３０ 円すいころ
３１ 小径側端面
３２ 大径側端面
４０ 保持器
Ａ1，Ａ2，Ａ3 潤滑油流路断面積[0001]
BACKGROUND OF THE INVENTION
The present invention relates to an oil lubricated tapered roller bearing used at high speed rotation.
[0002]
[Prior art]
2. Description of the Related Art Conventionally, there are tapered roller bearings that relatively rotate an inner ring and an outer ring around an axis by interposing a plurality of tapered rollers rotatably held by a cage between an inner ring and an outer ring.
[0003]
In a tapered roller bearing, it is important to sufficiently lubricate in order to prevent friction and seizure in each part. In particular, when used at high speed rotation, an oil lubrication method with excellent lubricity is employed.
[0004]
[Problems to be solved by the invention]
In the case of an oil-lubricated tapered roller bearing, during rotation, lubricating oil flows from the small-diameter bearing end of the tapered roller to the large-diameter bearing end of the tapered roller.
[0005]
When the lubricating oil flows through the bearing, the lubricating oil is agitated by the rolling of the tapered rollers. When the amount of lubricating oil staying inside the bearing increases, the stirring resistance increases and the loss torque of the bearing also increases.
[0006]
[Means for Solving the Problems]
The tapered roller bearing of the present invention includes an inner ring, an outer ring, and a plurality of tapered rollers rotatably held by a cage between the inner ring and the outer ring, and the inner ring is on the small diameter side of the tapered roller. The cage has a small flange portion projecting radially outward at the axial edge, and the retainer has an annular plate portion having a pocket for storing each tapered roller, and a small-diameter side edge of the tapered roller A flange portion formed by bending the annular plate portion inward in the radial direction, and an inner diameter side tip of the flange portion and an outer peripheral surface of the small collar portion of the inner ring with a gap between each other The lubricating oil flow passage cross-sectional area A 1 corresponding to the cross-sectional area excluding the cage between the axial end on the small diameter side of the outer ring and the small collar part of the inner ring, the coercive between the outer ring and the inner ring in the small-diameter side end surface Lubrication oil flow path cross-sectional area A 2, which corresponds to the cross-sectional area excluding vessel and the projected area of the tapered rollers and the small rib portion, of the large rib portion of the inner ring and the axial end portion of the large diameter side of the outer ring The lubricating oil flow passage cross-sectional area A 3 corresponding to the cross-sectional area excluding the cage and the tapered roller in the middle satisfies the relationship of A 1 ≦ A 2 <A 3 .
[0007]
According to the tapered roller bearing of the present invention, the lubricating oil passage sectional areas A 1 and A 2 on the inlet side where the lubricating oil enters the bearing are smaller than the lubricating oil passage sectional area A 3 on the outlet side where the lubricating oil exits from the bearing. It has become. Therefore, the amount of lubricating oil entering the bearing is less than the amount of lubricating oil exiting the bearing, and the amount of lubricating oil staying inside the bearing is reduced. As a result, the amount of lubricating oil agitated by the rolling of the tapered roller is reduced, and the loss torque of the bearing is reduced.
[0008]
DETAILED DESCRIPTION OF THE INVENTION
Hereinafter, an embodiment of the present invention will be described with reference to FIGS.
[0009]
1 is a partial longitudinal sectional view of a tapered roller bearing, FIG. 2 is a sectional view of a L 1 portion of a tapered roller bearing, FIG. 3 is a sectional view of a L 2 portion of the tapered roller bearing, and FIG. 4 is a L 3 portion of the tapered roller bearing. FIG. 5 is a graph showing a lubricating oil passage sectional area of a tapered roller bearing.
[0010]
In these drawings, 10 indicates an inner ring, 20 indicates an outer ring, 30 indicates a tapered roller, and 40 indicates a cage.
[0011]
The inner ring 10 is formed in an annular shape, and has a small flange portion 11 projecting radially outward at one end edge in a direction (axial direction) along the axis C, and projecting radially outward at the other end edge. A large collar portion 12 is provided. The outer peripheral surface (inner ring raceway surface) 13 of the inner ring 10 is formed in a tapered shape whose outer diameter gradually increases from the small collar part 11 to the large collar part 12. The large flange portion 12 is thick on the outer side in the radial direction, and the large-diameter side end surface 32 of the tapered roller 30 is in contact with the axial inner peripheral surface 12a.
[0012]
The outer ring 20 is formed in an annular shape having a larger diameter than the inner ring 10, and is disposed so as to face the inner ring raceway surface 13 of the inner ring 10 with a gap for holding the tapered rollers 30. An inner peripheral surface (outer ring raceway surface) 21 of the outer ring 20 is formed in a tapered shape whose inner diameter gradually increases from one end to the other end in the axial direction.
[0013]
The tapered roller 30 has a small-diameter side end surface 31, a large-diameter side end surface 32, and a tapered outer peripheral surface 33. The tapered roller 30 is brought into rolling contact with the inner ring raceway surface 13 and the outer ring raceway surface 21 with a part of the large-diameter side end surface 32 being brought into contact with the inner peripheral surface 12a of the large collar portion 12 of the inner ring 10. A plurality of tapered rollers 30 are equally distributed in the circumferential direction and are held rotatably by the cage 40.
[0014]
The cage 40 includes an annular plate portion 41 having a pocket for storing each tapered roller 30, and a flange portion 42 formed by bending the annular plate portion 41 radially inward at an end edge on the small diameter side of the tapered roller 30. And have.
[0015]
During the rotation of the tapered roller bearing, the lubricating oil flows from the axial end on the small diameter side of the tapered roller 30 to the axial end on the large diameter side of the tapered roller 30 (in the direction of arrow Q).
[0016]
2 to 4 show sectional views of the bearing in a section orthogonal to the axis M of the tapered roller 30 at each of the positions L 1 , L 2 and L 3 of the tapered roller bearing.
[0017]
In FIG. 2 to FIG. 4, the portions indicated by dots serve as flow path portions through which the lubricating oil passes.
[0018]
The lubricating oil flow passage cross-sectional area A 1 corresponds to the cross-sectional area of the small flange portion 11 excluding the cage 40 in the gap between the inner ring 10 and the outer ring 20.
[0019]
The lubricating oil passage cross-sectional area A 2 corresponds to a cross-sectional area excluding the projected areas of the cage 40, the tapered roller 30, and the small flange portion 11 in the gap between the inner ring 10 and the outer ring 20 on the small diameter side of the tapered roller 30. That is, the gavel portion 11 becomes a wall, and the lubricating oil flow passage cross-sectional area A 2 has a flow path area in which the projected area of the gavel portion 11 is also reduced.
[0020]
The lubricating oil flow passage cross-sectional area A 3 corresponds to the cross-sectional area of the large collar portion 12 excluding the cage 40 and the tapered roller 30 in the gap between the inner ring 10 and the outer ring 20.
[0021]
FIG. 5 shows the lubricating oil passage cross-sectional areas A 1 , A 2 , A 3 at the respective positions L 1 , L 2 , L 3 . In FIG. 5, the vertical axis represents the flow passage cross-sectional area of the lubricating oil, and the horizontal axis represents the position of the tapered roller bearing in the axial center C direction.
[0022]
The relationship between the lubricating oil passage cross-sectional areas A 1 , A 2 , A 3 of the tapered roller bearings at the respective positions L 1 , L 2 , L 3 is expressed by the following formula (1).
[0023]
A 1 ≦ A 2 <A 3 (1)
The shape of the retainer 40 is set so as to satisfy the relationship represented by the formula (1), the radial heights of the small flange portion 11 and the large flange portion 12 are set, and the tapered roller which is the inlet side of the lubricating oil A shielding plate is installed at the axial end on the small diameter side.
[0024]
In the present embodiment, by adjusting the radial heights of the small flange portion 11 and the large flange portion 12 and adjusting the radial length of the flange portion 42 of the retainer 40, the relationship shown in Expression (1) is obtained. Try to meet.
[0025]
As an example, the tapered roller bearing uses model number 30306DJ, the number of rollers of the tapered roller 30 is 14, the outer diameter of the small flange portion 11 is φ41.1 mm, the outer diameter of the large flange portion 12 is φ54 mm, and the cage 40 is a small flange. It is assumed that the flange portion 42 is formed by bending so that the inner diameter on the portion 11 side becomes smaller, and the inner diameter of the flange portion 42 is made substantially equal to the outer diameter of the small flange portion 11.
[0026]
Thereby, each lubricating oil flow-path cross-sectional area A becomes the following value.
[0027]
A 1 = 202.5mm 2
A 2 = 257.3 mm 2
A 3 = 357.3 mm 2
FIG. 5 will be described in detail.
[0028]
In FIG. 5, the flow passage cross-sectional area is reduced from the point a to the point b because of the flange portion 42 of the cage 40.
[0029]
The reason why the flow path cross-sectional area increases from the point b to the point c is that the crossing over the small flange portion 11 reaches the inner ring raceway surface 13.
[0030]
The fact that the cross-sectional area of the flow path decreases from the point c to the point d is due to the tapered roller 30.
[0031]
The reason why the flow path cross-sectional area increases from the point d to the point e is that the gap between the inner ring raceway surface 13 and the outer ring raceway surface 21 is tapered.
[0032]
The fact that the flow path cross-sectional area decreases from the point e to the point f is due to the large collar portion 12.
[0033]
Thereafter, the flow passage cross-sectional area increases as the passenger passes over the large collar portion 12.
[0034]
According to the tapered roller bearing configured as described above, the flow passage cross-sectional area A 1 and A 2 on the inlet side where the lubricating oil enters the bearing is smaller than the flow passage cross-sectional area A 3 on the outlet side where the lubricating oil exits from the bearing. ing. Thus, less than the oil quantity Q 2 of the lubricant oil amount to Q 1 lubricant exits from the bearing to enter the bearing, the amount of lubricating oil is reduced staying inside the bearing. As a result, the amount of lubricating oil stirred by the rolling of the tapered roller 30 is reduced, and the loss torque of the bearing is reduced.
[0035]
The structure of the tapered roller bearing is such that the bearing opening area A 1 at the axial end on the small diameter side of the tapered roller, the flow path cross-sectional area A 2 at the small diameter end surface of the tapered roller, and the axial end at the large diameter side of the tapered roller. The cross-sectional area A 3 of the part may be a structure satisfying the relationship of A 1 ≦ A 2 <A 3 .
[0036]
【The invention's effect】
According to the tapered roller bearing of the present invention, the agitation torque can be reduced and the loss torque of the bearing can be reduced.
[Brief description of the drawings]
FIG. 1 is a partial longitudinal sectional view of a tapered roller bearing according to an embodiment of the present invention.
FIG. 2 is a cross-sectional view of a portion L 1 of a tapered roller bearing according to an embodiment of the present invention.
FIG. 3 is a cross-sectional view of a portion L 2 of the tapered roller bearing according to the embodiment of the present invention.
FIG. 4 is a cross-sectional view of a portion L 3 of the tapered roller bearing according to the embodiment of the present invention.
FIG. 5 is a graph showing a lubricating oil passage cross-sectional area of a tapered roller bearing according to an embodiment of the present invention.
[Explanation of symbols]
DESCRIPTION OF SYMBOLS 10 Inner ring 11 Small collar part 12 Large collar part 13 Inner ring raceway surface 20 Outer ring 21 Outer ring raceway surface 30 Tapered roller 31 Small diameter side end surface 32 Large diameter side end surface 40 Cage A 1 , A 2 , A 3

Claims (2)

内輪と、外輪と、前記内輪と前記外輪の間に保持器によって回動自在に保持された複数の円すいころとを含み、
前記内輪は、前記円すいころの小径側における軸方向端縁において径方向外向きに突出させた小鍔部を有し、
前記保持器は、各円すいころを収納するポケットを有した環状板部と、前記円すいころの小径側の端縁において前記環状板部を径方向内向きに折曲してなるフランジ部とを有し、
前記フランジ部の内径側先端と前記内輪の小鍔部の外周面とが互いの間に隙間を介して対面しており、
前記外輪の小径側における軸方向端部と前記内輪の小鍔部との間における前記保持器を除いた断面積に相当する潤滑油流路断面積Ａ1、前記円すいころの小径側端面における前記外輪と前記内輪間における前記保持器と前記円すいころおよび前記小鍔部の投影面積を除いた断面積に相当する潤滑油流路断面積Ａ2、前記外輪の大径側における軸方向端部と前記内輪の大鍔部との間における前記保持器と前記円すいころを除いた断面積に相当する潤滑油流路断面積Ａ3が、
Ａ1≦Ａ2＜Ａ3
の関係を満たす、ことを特徴とする円すいころ軸受。An inner ring, an outer ring, and a plurality of tapered rollers rotatably held by a cage between the inner ring and the outer ring,
The inner ring has a small flange that protrudes radially outward at an axial end edge on the small diameter side of the tapered roller,
The cage includes an annular plate portion having a pocket for storing each tapered roller, and a flange portion formed by bending the annular plate portion radially inward at an end edge on the small diameter side of the tapered roller. And
The inner diameter side tip of the flange portion and the outer peripheral surface of the small collar portion of the inner ring face each other through a gap,
Lubricating oil channel cross-sectional area A 1 corresponding to the cross-sectional area excluding the cage between the axial end on the small-diameter side of the outer ring and the small collar portion of the inner ring, and the small-diameter side end surface of the tapered roller A lubricating oil flow passage cross-sectional area A 2 corresponding to a cross-sectional area excluding the projected area of the cage, the tapered roller and the small flange portion between the outer ring and the inner ring, an axial end on the large-diameter side of the outer ring, Lubricating oil channel cross-sectional area A 3 corresponding to the cross-sectional area excluding the cage and the tapered roller between the inner ring large collar part,
A 1 ≦ A 2 <A 3
Tapered roller bearings characterized by satisfying the above relationship. 内輪と、外輪と、前記内輪と前記外輪の間に保持器によって回動自在に保持された複数の円すいころとを含み、
前記内輪は、前記円すいころの小径側における軸方向端縁において径方向外向きに突出させた小鍔部と、前記円すいころの大径側における軸方向端縁において径方向外向きに突出させた大鍔部と、前記小鍔部から前記大鍔部にかけて外径が漸増するテーパ状の外周面からなる内輪軌道面とを有し、
前記外輪は、前記円すいころの小径側における軸方向端部から前記円すいころの大径側における軸方向端部にかけて内径が漸増するテーパ状の内周面からなる外輪軌道面を有し、
前記保持器は、各円すいころを収納するポケットを有した環状板部と、前記円すいころの小径側の端縁において前記環状板部を径方向内向きに折曲してなるフランジ部とを有し、
前記フランジ部の内径側先端と前記内輪の小鍔部の外周面とが互いの間に隙間を介して対面しており、
前記外輪の小径側における軸方向端部と前記内輪の小鍔部との間における前記保持器を除いた断面積に相当する潤滑油流路断面積Ａ1、前記円すいころの小径側端面における前記外輪と前記内輪間における前記保持器と前記円すいころおよび前記小鍔部の投影面積を除いた断面積に相当する潤滑油流路断面積Ａ2、前記外輪の大径側における軸方向端部と前記内輪の大鍔部との間における前記保持器と前記円すいころを除いた断面積に相当する潤滑油流路断面積Ａ3が、
Ａ1≦Ａ2＜Ａ3
の関係を満たす、ことを特徴とする円すいころ軸受。An inner ring, an outer ring, and a plurality of tapered rollers rotatably held by a cage between the inner ring and the outer ring,
The inner ring protruded radially outward at the axial end edge on the small diameter side of the tapered roller, and protruded radially outward at the axial end edge on the large diameter side of the tapered roller. A large collar part, and an inner ring raceway surface comprising a tapered outer peripheral surface whose outer diameter gradually increases from the small collar part to the large collar part,
The outer ring has an outer ring raceway surface composed of a tapered inner peripheral surface whose inner diameter gradually increases from an axial end on the small diameter side of the tapered roller to an axial end on the large diameter side of the tapered roller,
The cage includes an annular plate portion having a pocket for storing each tapered roller, and a flange portion formed by bending the annular plate portion radially inward at an end edge on the small diameter side of the tapered roller. And
The inner diameter side tip of the flange portion and the outer peripheral surface of the small collar portion of the inner ring face each other through a gap,
Lubricating oil channel cross-sectional area A 1 corresponding to the cross-sectional area excluding the cage between the axial end on the small-diameter side of the outer ring and the small collar portion of the inner ring, and the small-diameter side end surface of the tapered roller A lubricating oil flow passage cross-sectional area A 2 corresponding to a cross-sectional area excluding the projected area of the cage, the tapered roller and the small flange portion between the outer ring and the inner ring, an axial end on the large-diameter side of the outer ring, Lubricating oil channel cross-sectional area A 3 corresponding to the cross-sectional area excluding the cage and the tapered roller between the inner ring large collar part,
A 1 ≦ A 2 <A 3
Tapered roller bearings characterized by satisfying the above relationship.
JP2002233777A 2002-08-09 2002-08-09 Tapered roller bearing Expired - Fee Related JP4151347B2 (en)

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