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JP2004076766A - Tapered roller bearing - Google Patents

Tapered roller bearing Download PDF

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Publication number
JP2004076766A
JP2004076766A JP2002233777A JP2002233777A JP2004076766A JP 2004076766 A JP2004076766 A JP 2004076766A JP 2002233777 A JP2002233777 A JP 2002233777A JP 2002233777 A JP2002233777 A JP 2002233777A JP 2004076766 A JP2004076766 A JP 2004076766A
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JP
Japan
Prior art keywords
inner ring
outer ring
tapered roller
lubricating oil
flow path
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
JP2002233777A
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Japanese (ja)
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JP4151347B2 (en
Inventor
Hirobumi Momoji
百々路　博文
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Koyo Seiko Co Ltd
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Koyo Seiko Co Ltd
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
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Publication date
Application filed by Koyo Seiko Co Ltd filed Critical Koyo Seiko Co Ltd
Priority to JP2002233777A priority Critical patent/JP4151347B2/en
Publication of JP2004076766A publication Critical patent/JP2004076766A/en
Application granted granted Critical
Publication of JP4151347B2 publication Critical patent/JP4151347B2/en
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Classifications

    • 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)

Abstract

<P>PROBLEM TO BE SOLVED: To provide a tapered roller bearing of an oil lubrication type to be used with high speed rotation, having reduced stirring torque and less torque loss. <P>SOLUTION: The tapered roller bearing comprises an inner ring 10, an outer ring 20, and a plurality of tapered rollers 30 rotatably held between the inner ring 10 and the outer ring 20 by a cage 40. The inner ring 10 has a small collar portion 11, a large collar portion 12 and an inner ring raceway surface 13. The outer ring 20 has an outer ring raceway surface 21. A cross section area A<SB>1</SB>of a lubricating oil flow path between the axial end of the outer ring 20 at the side of its small diameter and the small collar portion 11 of the inner ring 10, a cross section area A<SB>2</SB>of the lubricating oil flow path between the outer ring 20 on the end face of the tapered roller 30 at the side of its small diameter and the inner ring, and a cross section area A<SB>3</SB>of the lubricating oil flow path between the axial end of the outer ring 20 at the side of its large diameter and the large collar portion 12 of the inner ring 10 are satisfied with a relationship A<SB>1</SB>≤A<SB>2</SB><A<SB>3</SB>. <P>COPYRIGHT: (C)2004,JPO

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の潤滑油流路断面積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の潤滑油流路断面積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の潤滑油流路断面積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]
TECHNICAL FIELD OF THE INVENTION
The present invention relates to an oil-lubricated tapered roller bearing used at high speed rotation.
[0002]
[Prior art]
BACKGROUND ART Conventionally, there has been a tapered roller bearing in which a plurality of tapered rollers rotatably held by a retainer are interposed between an inner ring and an outer ring to relatively rotate the inner ring and the outer ring about a shaft.
[0003]
In tapered roller bearings, it is important to provide sufficient lubrication in order to prevent friction and seizure in each part. In particular, when used at high speeds, an oil lubrication system having excellent lubricity is employed.
[0004]
[Problems to be solved by the invention]
In the case of an oil-lubricated tapered roller bearing, lubricating oil flows from the small-diameter bearing end of the tapered roller to the large-diameter bearing end of the tapered roller during rotation.
[0005]
When the lubricating oil flows through the bearing, the lubricating oil is stirred by the rolling of the tapered rollers. When the amount of lubricating oil staying inside the bearing increases, the stirring resistance increases, and the torque loss 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 retainer between the inner ring and the outer ring, and an axial end portion on a small diameter side of the outer ring. lubrication oil flow path cross-sectional area a 1, the lubricating oil flow path cross-sectional area a 2 between the said outer small-diameter side end face of the tapered roller inner ring, the large diameter side of the outer ring between the inner ring of the small rib portion and lubrication oil flow path cross-sectional area a 3 between the inner ring of the large rib portion and the axial end of the can satisfy the relation of a 1 ≦ a 2 <a 3 .
[0007]
According to the tapered roller bearing of the present invention, the lubricating oil flow path cross-sectional areas A 1 and A 2 on the inlet side where the lubricating oil enters the bearing are smaller than the lubricating oil flow path cross-sectional area A 3 on the outlet side where the lubricating oil exits the bearing. Has become. Therefore, the amount of lubricating oil entering the bearing is smaller than the amount of lubricating oil leaving the bearing, and the amount of lubricating oil remaining inside the bearing is reduced. As a result, the amount of lubricating oil stirred by the rolling of the tapered rollers decreases, and the torque loss of the bearing decreases.
[0008]
BEST MODE FOR CARRYING OUT THE INVENTION
An embodiment of the present invention will be described below with reference to FIGS.
[0009]
Figure 1 is a partial longitudinal sectional view of a tapered roller bearing, cross-sectional view, FIG. 3 is a cross-sectional view, FIG. 4 is L 3 portions of tapered roller bearings of L 2 portion of the tapered roller bearing of L 1 part of 2 tapered roller bearings FIG. 5 is a graph showing the sectional area of the lubricating oil flow path of the tapered roller bearing.
[0010]
In these figures, 10 is an inner ring, 20 is an outer ring, 30 is a tapered roller, and 40 is a retainer.
[0011]
The inner ring 10 is formed in a ring shape, and has a small flange portion 11 protruding radially outward at one end in a direction (axial direction) along the axis C, and protruding radially outward at the other end. It has a large collar portion 12. The outer peripheral surface (inner raceway surface) 13 of the inner ring 10 is formed in a tapered shape whose outer diameter gradually increases from the small flange portion 11 to the large flange portion 12. The large flange portion 12 has a large thickness on the radially outer side, and the large diameter side end surface 32 of the tapered roller 30 contacts the axially 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 arranged to face the inner ring raceway surface 13 of the inner ring 10 via a gap for holding the tapered rollers 30. The 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 in the axial direction to the other end.
[0013]
The tapered roller 30 has a small-diameter end face 31, a large-diameter end face 32, and a tapered outer peripheral face 33. The tapered roller 30 is brought into contact with the inner raceway surface 13 and the outer raceway surface 21 by bringing a part of the large diameter side end surface 32 into contact with the inner peripheral surface 12a of the large flange portion 12 of the inner race 10. The plurality of tapered rollers 30 are equally arranged in the circumferential direction, and are rotatably held by the holder 40.
[0014]
The retainer 40 includes an annular plate portion 41 having a pocket for accommodating each of the tapered rollers 30, and a flange portion 42 formed by bending the annular plate portion 41 radially inward at the small-diameter side edge of the tapered roller 30. And
[0015]
During rotation of the tapered roller bearing, lubricating oil flows from the small-diameter axial end of the tapered roller 30 to the large-diameter axial end of the tapered roller 30 (in the direction of arrow Q).
[0016]
2 to 4 show sectional views of the tapered roller bearing at respective positions L 1 , L 2 , and L 3 of the tapered roller 30 in a section orthogonal to the axis M of the tapered roller 30.
[0017]
In FIG. 2 to FIG. 4, portions indicated by dots are flow passage portions through which the lubricating oil passes.
[0018]
The lubricating oil flow path cross-sectional area A 1 corresponds to the cross-sectional area of the small flange 11 excluding the retainer 40 in the gap between the inner ring 10 and the outer ring 20.
[0019]
Lubrication oil flow path cross-sectional area A 2, in the small-diameter side of the tapered rollers 30, which corresponds to the cross-sectional area excluding the projected area of the cage 40 and the tapered rollers 30 and Shotsuba portion 11 in the gap of the inner ring 10 and outer ring 20. That is, the small rib portion 11 is a wall, and has a flow area projected area also reduced the lubrication oil flow path cross-sectional area A 2 in the small rib portion 11.
[0020]
Lubrication oil flow path cross-sectional area A 3, in the large rib portion 12, corresponding to the cross-sectional area excluding the retainer 40 and the tapered rollers 30 in the gap of the inner ring 10 and outer ring 20.
[0021]
FIG. 5 shows the sectional areas A 1 , A 2 , and A 3 of the lubricating oil flow paths at the respective positions L 1 , L 2 , and L 3 . 5, the vertical axis indicates the cross-sectional area of the flow path of the lubricating oil, and the horizontal axis indicates the position of the tapered roller bearing in the direction of the axis C.
[0022]
The relationship among the lubricating oil flow path cross-sectional areas A 1 , A 2 , and A 3 of the tapered roller bearings at the respective positions L 1 , L 2 , and L 3 is represented by the following equation (1).
[0023]
A 1 ≦ A 2 <A 3 (1)
The shape of the retainer 40, the radial height of the small flange portion 11 and the large flange portion 12, and the tapered roller on the lubricating oil inlet side are set so as to satisfy the relationship shown in Expression (1). A shielding plate is installed at the end in the axial direction on the small diameter side.
[0024]
In the present embodiment, by adjusting the radial height 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 a model number 30306DJ, the number of rollers of the tapered roller 30 is 14, the outer diameter of the small flange 11 is φ41.1 mm, the outer diameter of the large flange 12 is φ54 mm, and the retainer 40 is the small flange. The flange 42 is formed by bending the inner diameter of the part 11 side to be small, and the inner diameter of the flange 42 is substantially equal to the outer diameter of the small flange 11.
[0026]
Thus, the cross-sectional area A of each lubricating oil flow channel has the following value.
[0027]
A 1 = 202.5 mm 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 path cross-sectional area is reduced from point a to point b due to the flange portion 42 of the retainer 40.
[0029]
The reason why the cross-sectional area of the flow channel is increased from the point b to the point c is that the flow path crosses the small flange portion 11 and reaches the inner ring raceway surface 13.
[0030]
The cross-sectional area of the flow passage is reduced from point c to point d due to the tapered rollers 30.
[0031]
The reason that the flow path cross-sectional area increases from point d to point e is that the gap between the inner raceway surface 13 and the outer raceway surface 21 is tapered.
[0032]
The reason why the cross-sectional area of the flow channel is reduced from the point e to the point f is due to the large flange portion 12.
[0033]
Thereafter, as the vehicle gets over the large collar portion 12, the flow path cross-sectional area increases.
[0034]
According to the tapered roller bearing thus configured, the flow passage cross-sectional areas A 1 and A 2 on the inlet side where the lubricating oil enters the bearing are smaller than the flow passage cross-sectional area A 3 on the outlet side where the lubricating oil exits 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 rollers 30 decreases, and the torque loss of the bearing decreases.
[0035]
The structure of the tapered roller bearing includes a bearing opening area A 1 at the axial end on the small diameter side of the tapered roller, a flow path cross-sectional area A 2 at the small diameter side end face of the tapered roller, and an axial end on the large diameter side of the tapered roller. part of the flow path cross-sectional area a 3, may be a structure that satisfies the relation of a 1 ≦ a 2 <a 3 .
[0036]
【The invention's effect】
ADVANTAGE OF THE INVENTION According to the tapered roller bearing of this invention, reduction of stirring torque can be aimed at and the effect that loss torque of a bearing becomes small is acquired.
[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.
2 is a cross-sectional view of the L 1 portion of the tapered roller bearing in an embodiment of the present invention.
3 is a cross-sectional view of the L 2 portion of the tapered roller bearing in an embodiment of the present invention.
4 is a cross-sectional view of the L 3 portion of the tapered roller bearing in an embodiment of the present invention.
FIG. 5 is a graph showing a sectional area of a lubricating oil flow path of a tapered roller bearing according to an embodiment of the present invention.
[Explanation of symbols]
10 inner ring 11 small rib portion 12 large rib portion 13 the inner ring raceway surface 20 outer ring 21 outer ring raceway surface 30 tapered rollers 31 small diameter side end face 32 large diameter side end face 40 retainer A 1, A 2, A 3 lubrication oil flow path cross-sectional area

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の潤滑油流路断面積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の潤滑油流路断面積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の潤滑油流路断面積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 retainer between the inner ring and the outer ring,
Lubricating oil flow path cross-sectional area A 1 between the axial end on the small diameter side of the outer ring and the small flange of the inner ring, and the lubricating oil flow path between the outer ring and the inner ring on the small diameter end face of the tapered roller Area A 2 , the cross-sectional area A 3 of the lubricating oil flow path between the axial end on the large diameter side of the outer ring and the large flange of the inner ring,
A 1 ≦ A 2 <A 3
Tapered roller bearings that satisfy the following 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の潤滑油流路断面積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の潤滑油流路断面積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の潤滑油流路断面積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 retainer between the inner ring and the outer ring,
The inner ring has a small flange portion protruding radially outward at an axial edge on a small diameter side of the tapered roller, and a radially outward projection at an axial edge on a large diameter side of the tapered roller. A large collar portion, having an inner ring raceway surface composed of a tapered outer peripheral surface having an outer diameter gradually increasing from the small collar portion to the large collar portion,
The outer ring has an outer ring raceway surface formed of a tapered inner peripheral surface whose inner diameter gradually increases from an axial end on a small diameter side of the tapered roller to an axial end on a large diameter side of the tapered roller,
Lubricating oil flow path cross-sectional area A 1 between the axial end on the small diameter side of the outer ring and the small flange of the inner ring, and the lubricating oil flow path between the outer ring and the inner ring on the small diameter end face of the tapered roller Area A 2 , the cross-sectional area A 3 of the lubricating oil flow path between the axial end on the large diameter side of the outer ring and the large flange of the inner ring,
A 1 ≦ A 2 <A 3
Tapered roller bearings that satisfy the following relationship:
JP2002233777A 2002-08-09 2002-08-09 Tapered roller bearing Expired - Fee Related JP4151347B2 (en)

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EP1967749A2 (en) 2007-03-05 2008-09-10 JTEKT Corporation Tapered roller bearing with lubrication
US7645074B2 (en) 2005-04-28 2010-01-12 Jtekt Corporation Fluid-lubricated type tapered roller bearing device and vehicle pinion shaft supporting assembly
CN107559312A (en) * 2016-06-30 2018-01-09 株式会社捷太格特 Taper roll bearing
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US7645074B2 (en) 2005-04-28 2010-01-12 Jtekt Corporation Fluid-lubricated type tapered roller bearing device and vehicle pinion shaft supporting assembly
EP1967749A2 (en) 2007-03-05 2008-09-10 JTEKT Corporation Tapered roller bearing with lubrication
US7950856B2 (en) 2007-03-05 2011-05-31 Jtekt Corporation Tapered roller bearing
CN107559312A (en) * 2016-06-30 2018-01-09 株式会社捷太格特 Taper roll bearing
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US10180161B2 (en) 2016-11-17 2019-01-15 Jtekt Corporation Tapered roller bearing

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