JP7495816B2 - Tapered roller bearings - Google Patents
Tapered roller bearings Download PDFInfo
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- JP7495816B2 JP7495816B2 JP2020096727A JP2020096727A JP7495816B2 JP 7495816 B2 JP7495816 B2 JP 7495816B2 JP 2020096727 A JP2020096727 A JP 2020096727A JP 2020096727 A JP2020096727 A JP 2020096727A JP 7495816 B2 JP7495816 B2 JP 7495816B2
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- raceway surface
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- 230000002093 peripheral effect Effects 0.000 claims description 8
- 210000000078 claw Anatomy 0.000 claims description 6
- 238000005096 rolling process Methods 0.000 description 25
- 238000010586 diagram Methods 0.000 description 4
- 238000005452 bending Methods 0.000 description 2
- 238000013461 design Methods 0.000 description 2
- 238000000034 method Methods 0.000 description 2
- 229910000831 Steel Inorganic materials 0.000 description 1
- 239000003638 chemical reducing agent Substances 0.000 description 1
- 238000010276 construction Methods 0.000 description 1
- 238000011156 evaluation Methods 0.000 description 1
- 238000003780 insertion Methods 0.000 description 1
- 230000037431 insertion Effects 0.000 description 1
- 239000000463 material Substances 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 239000011347 resin Substances 0.000 description 1
- 229920005989 resin Polymers 0.000 description 1
- 230000003068 static effect Effects 0.000 description 1
- 239000010959 steel Substances 0.000 description 1
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C19/00—Bearings with rolling contact, for exclusively rotary movement
- F16C19/22—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings
- F16C19/34—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load
- F16C19/36—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load with a single row of rollers
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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
- F16C33/34—Rollers; Needles
- F16C33/36—Rollers; Needles with bearing-surfaces other than cylindrical, e.g. tapered; with grooves in the bearing surfaces
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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
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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
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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
- F16C33/58—Raceways; Race rings
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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
- F16C43/00—Assembling bearings
- F16C43/04—Assembling rolling-contact bearings
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Rolling Contact Bearings (AREA)
- Mounting Of Bearings Or Others (AREA)
Description
この発明は、ロボットや建設機械の減速機で使用される円すいころ軸受、特に、外輪の外輪軌道面の小径側端部と大径側端部、および内輪の内輪軌道面の小径側端部と大径側端部の4つの端部のうち、外輪の外輪軌道面の大径側端部に半径方向内方に突出する鍔部を形成した、外輪鍔形式の円すいころ軸受に関するものである。 This invention relates to tapered roller bearings used in the reducers of robots and construction machinery, and in particular to tapered roller bearings of the outer ring flange type, in which a flange protruding radially inward is formed on the large diameter end of the outer ring raceway surface of the outer ring, out of the four ends: the small diameter end and large diameter end of the outer ring raceway surface of the outer ring, and the small diameter end and large diameter end of the inner ring raceway surface of the inner ring.
内輪の内輪軌道面の大径側端部に鍔部を形成しないで、外輪の外輪軌道面の大径側端部にのみ半径方向内方に突出する鍔部を形成した外輪鍔形式の円すいころ軸受は、特許文献1または特許文献2に開示はされているものの、製品として実用化されているものはほとんど見かけない。
An outer ring rib type tapered roller bearing in which a rib is not formed on the large diameter end of the inner ring raceway of the inner ring, and a rib protruding radially inward is formed only on the large diameter end of the outer ring raceway of the outer ring is disclosed in
その理由としては、内輪の内輪軌道面の大径側端部に鍔部を形成した内輪鍔形式の円すいころ軸受に比べ、外輪の外輪軌道面の大径側端部に鍔部を形成した外輪鍔形式の円すいころ軸受は、純アキシャル荷重の負荷能力が極端に下がるということが一番に挙げられる。
ところで、一般的に円すいころ軸受において、モーメント剛性と軸受寿命を向上させるには、ころサイズ(ころ径)を大きくすることが有効である。
The primary reason for this is that, compared to an inner ring rib type tapered roller bearing in which a rib is formed on the large diameter end of the inner ring raceway surface of the inner ring, an outer ring rib type tapered roller bearing in which a rib is formed on the large diameter end of the outer ring raceway surface of the outer ring has an extremely reduced load capacity for pure axial loads.
Generally, in order to improve the moment rigidity and bearing life of a tapered roller bearing, it is effective to increase the roller size (roller diameter).
ところが、外輪鍔形式の円すいころ軸受の場合、軸受断面高さと軸受PCDを同じにしてころサイズを大きくすると、外輪鍔部の肉厚が薄くなるため、外輪鍔部の強度低下が懸念され、実用化することが困難となる。 However, in the case of tapered roller bearings with outer ring ribs, if the bearing cross-sectional height and bearing PCD are kept the same and the roller size is increased, the thickness of the outer ring rib becomes thinner, which raises concerns about a decrease in the strength of the outer ring rib, making it difficult to put into practical use.
そこで、この発明は、内輪鍔形式の円すいころ軸受に比べ純アキシャル荷重の負荷能力を極端に低くすることなく、十分なモーメント荷重と軸受寿命を有し、しかも外輪鍔部の強度低下の懸念もない、実用化可能な外輪鍔形式の円すいころ軸受の設計基準を見出すことを課題とするものである。 The objective of this invention is to find design criteria for a practical outer ring rib type tapered roller bearing that has sufficient moment load and bearing life without drastically reducing the load capacity of pure axial load compared to an inner ring rib type tapered roller bearing, and that does not involve concerns about reduced strength of the outer ring rib.
前記の課題を解決するために、この発明は、ころ径と外輪鍔部の肉厚との関係に着目し、ころ径と外輪鍔部の肉厚の関係を所定の数値範囲にすることによって、内輪鍔形式の円すいころ軸受と比べても純アキシャル荷重の負荷能力が極端に低くなく、そして十分なモーメント荷重と軸受寿命を有し、しかも外輪鍔部の強度低下の懸念もない、実用化可能な外輪鍔形式の円すいころ軸受を得ることができるといことを見出したのである。 In order to solve the above problems, this invention focuses on the relationship between the roller diameter and the thickness of the outer ring rib, and has discovered that by setting the relationship between the roller diameter and the thickness of the outer ring rib within a specified numerical range, it is possible to obtain a practical outer ring rib type tapered roller bearing that has a load capacity for pure axial loads that is not extremely low compared to inner ring rib type tapered roller bearings, has sufficient moment loads and bearing life, and is free of concerns about a decrease in the strength of the outer ring rib.
すなわち、この発明は、内周面に外輪軌道面を有する外輪と、外周面に内輪軌道面を有する内輪と、前記外輪軌道面と前記内輪軌道面との間に転動自在に配置される複数の円すいころと、この複数の円すいころを所定の間隔で収容保持する複数のポケットを有する保持器とを備え、前記外輪の外輪軌道面の小径側端部と大径側端部、および内輪の内輪軌道面の小径側端部と大径側端部の4つの端部のうち、外輪の外輪軌道面の大径側端部に半径方向内方に突出する鍔部を形成した円すいころ軸受において、接触角を40°~50°とし、外輪鍔の肉厚Eところ大径側径Dwとの関係を、0.19<E/Dw<0.44を満足させるというものである。 That is, this invention relates to a tapered roller bearing comprising an outer ring having an outer ring raceway surface on its inner peripheral surface, an inner ring having an inner ring raceway surface on its outer peripheral surface, a number of tapered rollers arranged to roll freely between the outer ring raceway surface and the inner ring raceway surface, and a cage having a number of pockets that house and hold the tapered rollers at predetermined intervals, and in which a rib protruding radially inward is formed at the large diameter end of the outer ring raceway surface of the outer ring out of four ends: the small diameter end and large diameter end of the outer ring raceway surface of the outer ring, and the small diameter end and large diameter end of the inner ring raceway surface of the inner ring, the contact angle is 40° to 50°, and the relationship between the thickness E of the outer ring rib and the roller large diameter side diameter Dw satisfies 0.19 < E/Dw < 0.44.
なお、この発明において、接触角とは、軸受中心軸と外輪軌道面のなす角度、外輪鍔部の肉厚Eとは外輪軌道面と外輪鍔面の接点から軸受外径面までの距離、ころ大径側径Dwとは円すいころの大径側端面の直径をいうものとする。 In this invention, the contact angle is the angle between the bearing center axis and the outer ring raceway surface, the thickness E of the outer ring rib is the distance from the contact point between the outer ring raceway surface and the outer ring rib surface to the outer diameter surface of the bearing, and the large diameter side diameter Dw of the roller is the diameter of the large diameter side end face of the tapered roller.
円すいころ軸受の径方向サイズを一定、すなわち、軸受断面高さHと軸受外径Dを一定にして、ころサイズ(ころ径)を大きくすると、負荷容量Crが大きくなり、軸受寿命とモーメント剛性を高くすることができても、ころサイズを大きくすることにより、外輪鍔の肉厚Eが薄くなって、鍔部の強度が低下し、過大荷重を受けることで鍔部の割れが発生する懸念があるが、この発明で規定する数値規定を満足するように外輪鍔形式の円すいころ軸受の設計を行うことにより、すなわち、接触角を40°~50°とし、外輪鍔の肉厚Eところ大径側径Dwとの関係を、0.19<E/Dw<0.44を満足させれば、内輪鍔形式の円すいころ軸受と比べても純アキシャル荷重の負荷能力が極端に低くなく、十分なモーメント荷重と軸受寿命を有し、しかも外輪鍔部の強度低下の懸念もない、外輪鍔部の円すいころ軸受が得られる。 If the radial size of a tapered roller bearing is constant, that is, if the bearing cross-sectional height H and bearing outer diameter D are constant, and the roller size (roller diameter) is increased, the load capacity Cr increases, and the bearing life and moment rigidity can be increased. However, by increasing the roller size, the thickness E of the outer ring rib becomes thinner, reducing the strength of the rib and raising the concern that the rib may crack due to excessive load. However, by designing an outer ring rib type tapered roller bearing to satisfy the numerical specifications stipulated in this invention, that is, by setting the contact angle to 40° to 50° and satisfying the relationship between the outer ring rib thickness E and the roller large diameter side diameter Dw of 0.19 < E/Dw < 0.44, a tapered roller bearing with an outer ring rib that has a pure axial load capacity that is not extremely low compared to an inner ring rib type tapered roller bearing, has sufficient moment load and bearing life, and is free of concerns about reduced strength of the outer ring rib.
以下、この発明の実施の形態を添付図面に基づいて説明する。 The following describes an embodiment of the present invention with reference to the attached drawings.
この発明の実施形態に係る円すいころ軸受11は、図3に示すように、内周面に外輪軌道面12aを有する外輪12と、外周面に内輪軌道面13aを有する内輪13と、前記外輪軌道面12aと前記内輪軌道面13aとの間に転動自在に配置される複数の円すいころ14と、この複数の円すいころ14を所定の間隔で収容保持する複数のポケットを有する保持器15とを備え、前記外輪12の外輪軌道面12aの小径側端部と大径側端部、および内輪13の内輪軌道面13aの小径側端部と大径側端部の4つの端部のうち、外輪12の外輪軌道面12aの大径側端部に半径方向内方に突出する鍔部12bを形成した、外輪鍔形式のものである。
As shown in FIG. 3, the tapered roller bearing 11 according to the embodiment of the present invention comprises an
この発明に係る円すいころ軸受11は、内輪13の小径側端部の小鍔をなくし、小鍔の分だけころ長さを長くして高負荷容量化を図ると共に、外輪12の外輪軌道面12aの大径側端部に半径方向内方に突出する鍔部12bを形成し、内輪13の内輪軌道面13aの大径側端部の鍔部をなくしている。
The tapered roller bearing 11 of this invention eliminates the small flange at the small diameter end of the
この発明の円すいころ軸受11は、接触角αを40°~50°の急こう配に設定して高モーメント剛性化を図っており、図3の実施形態に係る円すいころ軸受11は、接触角αを45°に設定している。 The tapered roller bearing 11 of this invention has a contact angle α set at a steep gradient of 40° to 50° to achieve high moment rigidity, and the tapered roller bearing 11 of the embodiment shown in Figure 3 has a contact angle α set at 45°.
接触角が40°~50°の急こう配の円すいころ軸受11は、外輪12の外輪軌道面12aの大径側端部と内輪13の大径側の端面との間に軸方向に大きなスペースが空くので、このスペースを利用してこの発明では半径方向内方に突出する鍔部12bを形成している。
In a tapered roller bearing 11 with a steep contact angle of 40° to 50°, a large space is created in the axial direction between the large-diameter end of the outer
外輪12の外輪軌道面12aの大径側端部に半径方向内方に突出する鍔部12bを形成し、内輪13の内輪軌道面13aの大径側端部の鍔部をなくすことにより、軸方向のコンパクト化を図ることができる。
By forming a
即ち、図3に2点鎖線で示すように、内輪13の内輪軌道面13aの大径側端部に鍔部12bを形成した場合の軸方向幅をT’とすると、内輪13の内輪軌道面13aの大径側端部の鍔部をなくすことによって、内輪13の軸方向幅を薄くすることができ、外輪12の外輪軌道面12aの大径側端部に半径方向内方に突出する鍔部12bを形成した場合の軸方向幅がTであるから、T’-Tの分だけ軸方向幅をコンパクトにすることができる。
In other words, as shown by the two-dot chain line in Figure 3, if the axial width when a
この発明のように、外輪12の外輪軌道面12aの大径側端部に半径方向内方に突出する鍔部12bを形成することにより、内輪13の内輪軌道面13aの大径側端部に鍔部を形成する図11に示す内輪鍔形式の円すいころ軸受1に比し、鍔部を高剛性化できる。
As in this invention, by forming a
即ち、図3に示すように、外輪12の外輪軌道面12aの大径側端部に半径方向内方に突出する鍔部12bを形成する場合と、図12に示すように、内輪3の内輪軌道面3aの大径側端部に鍔部3bを形成する場合とを比較すると、鍔部の高さC(軌道面と鍔面の交点と鍔部頂点からなる径方向の距離)が同じだとしても、図6に示すころ端面と外輪鍔面との接触面積は、図14に示す内輪鍔形式の円すいころ軸受におけるころ端面と内輪鍔面との接触面積よりも約7%大きくなり、ころに発生する誘起スラスト力を受ける面積が外輪鍔形式の方が大きくなるので、接触部の応力が低くなり、ころ端面と鍔面の接触ひずみが小さくなる。
In other words, when comparing the case where a
また、図12に示す内輪鍔形式の円すいころ軸受のように、内輪3の大径側端部に鍔部3bを設けると、円すいころ4に発生する誘起スラスト力は、図13に白抜き矢印で示すように、鍔部3bで受けることになり、鍔部3bに掛かる曲げ応力によって鍔部3bにひずみが生じる可能性があるが、外輪鍔形式の円すいころ軸受は、図5に白抜き矢印で示すように、円すいころ14に発生する誘起スラスト力は、外輪12の鍔部12bに掛かる曲げ応力をハウジング6で受けることができるため、鍔部12bの剛性が高くなる。図12の内輪鍔形式の円すいころ軸受において、符号2は外輪、2aは外輪軌道面、5は保持器を示している。
In addition, as in the inner ring flange type tapered roller bearing shown in FIG. 12, when a
この発明は、接触角を40°~50°とし、外輪鍔の肉厚Eところ大径側径Dwとの関係を、0.19<E/Dw<0.44を満足するように設定することにより、内輪の内輪軌道面の大径側端部に鍔部を形成したものと比べて純アキシャル荷重の負荷能力を極端に低くすることなく、十分なモーメント荷重と軸受寿命を有し、しかも外輪鍔部の強度低下の懸念もない、外輪鍔形式の円すいころ軸受を得るようにしたものである。 This invention achieves an outer ring rib type tapered roller bearing that has a contact angle of 40° to 50° and a relationship between the outer ring rib thickness E and the roller large diameter Dw that satisfies 0.19 < E/Dw < 0.44, thereby providing sufficient moment load and bearing life without drastically reducing the load capacity of pure axial load compared to a bearing with a rib formed on the large diameter end of the inner ring raceway surface of the inner ring, and without the risk of a decrease in the strength of the outer ring rib.
ここで、ころ径(ころ大径側径Dw)と外輪鍔の肉厚Eの関係はE/Dwで表しており、この値が大きいほど外輪鍔の肉厚Eが厚く、ころ大径側径Dwが小さいことを表している。 The relationship between the roller diameter (large-diameter roller diameter Dw) and the thickness E of the outer ring rib is expressed as E/Dw, and the larger this value is, the thicker the thickness E of the outer ring rib is and the smaller the large-diameter roller diameter Dw is.
この発明の円すいころ軸受11は、接触角が40°~50°であるが、外部荷重を一定とし、また軸受のPCDところのサイズと個数は一定で接触角のみを変化させたときのモーメント剛性は図10のグラフのとおりであり、また、寿命比は図11に示すグラフのとおりである。この図10と図11のグラフから各接触角に対する総合評価を行うと表1に示すとおりとなり、接触角を40~50°にすることにより、軸受のモーメント剛性と寿命を両立させることができるということが確認できた。
Tapered roller bearing 11 of this invention has a contact angle of 40° to 50°, and when the external load is kept constant, and the PCD and roller size and number of the bearing are constant, and only the contact angle is changed, the moment stiffness is as shown in the graph in Figure 10, and the life ratio is as shown in the graph in Figure 11. When a comprehensive evaluation of each contact angle is made from the graphs in Figures 10 and 11, the results are as shown in Table 1, and it was confirmed that by setting the contact angle to 40° to 50°, it is possible to achieve both moment stiffness and life of the bearing.
この発明において、外輪鍔の肉厚Eところ大径側径Dwとの関係を、0.19<E/Dw<0.44にするという数値規定は、軸受の径方向サイズ一定、すなわち、軸受断面高さH、軸受外径Dを一定として、接触角αを変えながら、モーメント荷重、軸受寿命及び鍔強度の比較を行った表2~表4の結果より求めたものである。 In this invention, the numerical specification that the relationship between the outer ring flange thickness E and the roller large diameter Dw is 0.19 < E/Dw < 0.44 was obtained from the results in Tables 2 to 4, in which the radial size of the bearing was kept constant, i.e., the bearing cross-sectional height H and the bearing outer diameter D were kept constant, and the contact angle α was changed to compare the moment load, bearing life, and flange strength.
なお、表2~表4において、寿命とモーメント剛性の〇は、実用可能(寿命が長い、モーメント剛性が高い)な領域を表し、×は〇に対して軸受機能への信頼性が低い(寿命が短い、モーメント剛性が低い)領域を示している。
また、鍔強度に於いては、〇は安全率1.2以上を示し信頼性が高く、×は安全率1.2未満を示し、信頼性が低い領域を示している。
In Tables 2 to 4, ◯ for life and moment stiffness indicates a practical range (long life, high moment stiffness), while × indicates a range where the bearing function is less reliable (shorter life, low moment stiffness) compared to ◯.
In addition, in terms of flange strength, ◯ indicates a safety factor of 1.2 or more, which means high reliability, while × indicates a safety factor of less than 1.2, which means a region of low reliability.
なお、鍔強度の安全率の定義は以下通りである。
鍔強度の安全率=軸受の静定格ラジアル荷重C0r相当を軸受に負荷したときの鍔部に発生する
最大応力/一般軸受鋼の疲労限許容応力
を示すものである。
この安全率1.2の基準は、「日本機械学会_疲労強度の設計資料」にも記載されているとおり、疲労強度の安全率基準として鉄道車両や自動車など幅広い分野で使用されている汎用的なものである。
The safety factor of the flange strength is defined as follows:
Safety factor of flange strength = Maximum stress generated in the flange when the bearing is loaded with a static rated radial load C0r / Allowable fatigue stress for general bearing steel.
This safety factor of 1.2 standard, as stated in the "Japan Society of Mechanical Engineers - Fatigue Strength Design Materials," is a general-purpose safety factor standard for fatigue strength that is used in a wide range of fields, including railway vehicles and automobiles.
表2~表4において、軸受寿命、モーメント剛性及び鍔強度が〇であるE/Dwの範囲は、2重線で囲む、接触角40°で0.19~0.46、接触角45°で0.19~0.45、接触角50°で0.18~0.44である。
この表2~表4において2重線で囲む範囲が、すなわち、接触角40~50°における0.19<E/Dw<0.44の範囲内が、寿命かつモーメント剛性の性能が高く、鍔強度及び安全率が高い領域となる。
In Tables 2 to 4, the ranges of E/Dw where the bearing life, moment rigidity and flange strength are ◯ are surrounded by double lines and are 0.19 to 0.46 at a contact angle of 40°, 0.19 to 0.45 at a contact angle of 45°, and 0.18 to 0.44 at a contact angle of 50°.
The range enclosed by the double line in Tables 2 to 4, that is, the range of 0.19<E/Dw<0.44 for a contact angle of 40 to 50°, is the region in which the life and moment rigidity performance are high, and the flange strength and safety factor are high.
円すいころ軸受の場合、ころサイズ、ころ本数、接触角、ころ角度、鍔部に対するころの接点位置と鍔側軌道面との角度xが同じ諸元の場合、内輪の内輪軌道面の大径側端部に鍔部を形成した図2に示すもの(以下、「内輪鍔軸受」という。)と、外輪の外輪軌道面の大径側端部に鍔部を形成した図1に示すもの(以下、「外輪鍔軸受」という。)を比較すると、純アキシャル(Fa)負荷時に、外輪鍔軸受の方が、内輪鍔軸受よりも転動体荷重(外輪側転動体荷重Fo、内輪側転動体荷重Fi)及び転動体と軌道輪との接触面圧が増加するが、この発明のように、接触角を40°~50°とし、且つ、ころ角度を3.5°以下にした場合、純アキシャル(Fa)負荷時の転動体荷重(外輪側転動体荷重Fo、内輪側転動体荷重Fi)及び軌道輪との接触面圧の増加を抑制し、純ラジアル(Fr)負荷時の転動体荷重及び軌道輪との接触面圧も抑制することができる。 In the case of tapered roller bearings, when the roller size, number of rollers, contact angle, roller angle, and angle x between the contact point of the roller with the rib and the rib side raceway surface are the same, a comparison is made between a bearing as shown in Figure 2 in which a rib is formed on the large diameter end of the inner ring raceway surface of the inner ring (hereafter referred to as an "inner ring rib bearing") and a bearing as shown in Figure 1 in which a rib is formed on the large diameter end of the outer ring raceway surface of the outer ring (hereafter referred to as an "outer ring rib bearing"), and the results show that under pure axial (Fa) load, the outer ring rib bearing is stronger than the inner ring rib bearing. The rolling element load (outer ring side rolling element load Fo, inner ring side rolling element load Fi) and the contact surface pressure between the rolling element and the raceway increase, but if the contact angle is set to 40°-50° and the roller angle is set to 3.5° or less, as in this invention, the increase in the rolling element load (outer ring side rolling element load Fo, inner ring side rolling element load Fi) and the contact surface pressure with the raceway during a pure axial (Fa) load can be suppressed, and the rolling element load and the contact surface pressure with the raceway during a pure radial (Fr) load can also be suppressed.
図1に示す外輪鍔軸受と図2に示す内輪鍔軸受における純アキシャル負荷時の転動体荷重の算出式は、
Fio:外輪側の転動体荷重(内輪鍔軸受)
Foo:外輪側の転動体荷重(外輪鍔軸受)
Fii:内輪側の転動体荷重(内輪鍔軸受)
Foi:内輪側の転動体荷重(外輪鍔軸受)
Fir:鍔側の転動体荷重(内輪鍔軸受)
For:鍔側の転動体荷重(外輪鍔軸受)
α:軸受中心軸と外輪軌道面のなす角度
θ:軸受中心軸と内輪軌道面のなす角度
β:ころ角度
x:鍔部に対するころの接点位置と鍔側軌道面との角度
Y:ころ大端面と内輪鍔部との接点角度(θ+x)
δ:ころ大端面と外輪鍔部との接点角度(α-x)
とした場合に、次のようになる。
Fio=Fa/sinα
Foo=Foi(sinθ・sinδ+cosθ・cosδ)/(cosα・cosδ+sinα・sinδ)
Fii=Fio(sinα・sinY+cosα・cosY)/(cosθ・cosY+sinθ・sinY)
Foi=Fa/sinθ
Fir=(Fiicosθ-Fiocosα)/sinY
For=(Foicosθ-Foocosα)/sinδ
The formula for calculating the rolling element load when a pure axial load is applied to the outer ring flange bearing shown in FIG. 1 and the inner ring flange bearing shown in FIG. 2 is as follows:
Fio: Rolling element load on the outer ring side (inner ring flange bearing)
Foo: Rolling element load on the outer ring side (outer ring flange bearing)
Fii: Rolling element load on the inner ring side (inner ring flange bearing)
Foi: Rolling element load on the inner ring side (outer ring flange bearing)
Fir: Rolling element load on flange side (inner ring flange bearing)
For: Rolling element load on flange side (outer ring flange bearing)
α: Angle between the bearing center axis and the outer ring raceway surface θ: Angle between the bearing center axis and the inner ring raceway surface β: Roller angle x: Angle between the contact point of the roller with the rib and the rib side raceway surface
Y: Contact angle between the roller large end face and the inner ring rib (θ + x)
δ: Contact angle between roller large end face and outer ring rib (α-x)
In this case, the result is as follows:
Fio = Fa / sin α
Foo = Foi (sinθ sinδ + cosθ cosδ) / (cosα cosδ + sinα sinδ)
Fii = Fio (sinα sinY + cosα cosY) / (cosθ cosY + sinθ sinY)
Foi = Fa / sin θ
Fir = (Ficosθ - Ficosα) / sinY
For = (Focosθ - Focosα) / sinδ
上記の計算式により、純アキシャル荷重Faを負荷して、接触角が40°~50°で、ころ角度を3.5°以下にした各例と、接触角が40°以下で、ころ角度が3.5°以上にした各例について、最大転動体荷重と最大接触面圧を求めると、表5~表11のとおりとなる。 Using the above formula, the maximum rolling element load and maximum contact surface pressure are calculated for each example where a pure axial load Fa is applied, the contact angle is between 40° and 50°, and the roller angle is 3.5° or less, and for each example where the contact angle is 40° or less and the roller angle is 3.5° or more, and the results are shown in Tables 5 to 11.
前記表5~表11の結果から、軸受寸法が同一の外輪鍔軸受と内輪鍔軸受とについて、内輪鍔軸受の最大転動体荷重及び最大接触面圧を100%にして比較すると、この発明で規定される外輪鍔軸受は、最大転動体荷重及び最大接触面圧を共に、内輪鍔軸受の10%以内の増加率に抑制できるのに対し、この発明の規定外の外輪鍔軸受は、最大転動体荷重及び最大接触面圧の少なくとも一方が、内輪鍔軸受よりも増加率が10%を超えるということが確認された。 From the results of Tables 5 to 11, it was confirmed that when comparing outer ring rib bearings and inner ring rib bearings with the same bearing dimensions, with the maximum rolling element load and maximum contact surface pressure of the inner ring rib bearing set at 100%, the outer ring rib bearings specified in this invention can suppress the increase rate of both the maximum rolling element load and the maximum contact surface pressure to within 10% of the inner ring rib bearing, whereas the outer ring rib bearings not specified in this invention have an increase rate of more than 10% in at least one of the maximum rolling element load and maximum contact surface pressure compared to the inner ring rib bearing.
この発明において、保持器15としては、樹脂製のものを使用することができる。
In this invention, the
保持器15は、図7および図8に示すように、大径側に大径リング部15aと、小径側に小径リング部15bを有し、外径部に円すいころ14を案内するころ案内面15cを有し、内径面に円すいころ14を保持する爪15dを有する。円すいころ14を案内するころ案内面15cと円すいころ14を保持する爪15dは逆でもよい。また、保持器15の大径リング部15aの外周面に、外輪12の鍔部12bとの干渉を避ける切欠き部15eを設けている。
As shown in Figures 7 and 8, the
図7に示すように、円すいころ14を保持器15の外径側にあるころ案内面15cに押し当てたときのころ外接円径をPとし、図7に示すように、保持器15の内径側の爪15dに円すいころ14を押し当てたときのころ外接円径をP’とした場合、図9(a)(b)(c)に示す手順で、ころ-保持器アッシーを外輪12に挿入する際に、鍔部12bの鍔高さCが同一で、接触角αと、鍔外径角度γ、|P-P’|を各種変更し、ころ-保持器アッシーの外輪12への挿入のし易さを判定した結果を表13~表17に示す。
表12~表16の結果から、接触角が40~50°のものは、|P-P’|≧C、且つ、鍔外径角度γが35°~50°の場合において、ころ-保持器アッシーの外輪12への挿入性が良好であるということが確認できた。
As shown in Figure 7, if the roller circumscribing circle diameter when the tapered
From the results in Tables 12 to 16, it was confirmed that when the contact angle is 40 to 50°, |P-P'|≧C, and the flange outer diameter angle γ is 35° to 50°, the roller-retainer assembly has good insertability into the
この発明は前述した実施形態に何ら限定されるものではなく、この発明の要旨を逸脱しない範囲において、さらに種々の形態で実施し得ることは勿論のことであり、本発明の範囲は、特許請求の範囲によって示され、さらに特許請求の範囲に記載の均等の意味、および範囲内の全ての変更を含む。 This invention is not limited to the above-described embodiment, and can of course be embodied in various other forms without departing from the spirit of the invention. The scope of the invention is indicated by the claims, and further includes the equivalent meanings set forth in the claims, and all modifications within the scope of the claims.
11 :軸受
12 :外輪
12a :外輪軌道面
12b :鍔部
13 :内輪
13a :内輪軌道面
15 :保持器
15a :大径リング部
15b :小径リング部
15c :案内面
15d :爪
15e :切欠き部
11: Bearing 12:
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JP2007187308A (en) | 2005-12-16 | 2007-07-26 | Ntn Corp | Bearing device for wheel |
JP2008309270A (en) | 2007-06-15 | 2008-12-25 | Ntn Corp | Tapered roller bearing |
JP2016200227A (en) | 2015-04-10 | 2016-12-01 | Ntn株式会社 | Conical roller bearing |
JP2019173841A (en) | 2018-03-28 | 2019-10-10 | Ntn株式会社 | Conical roller bearing |
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JP6388191B2 (en) * | 2012-12-25 | 2018-09-12 | 日本精工株式会社 | Tapered roller bearings |
US11460071B2 (en) * | 2018-12-07 | 2022-10-04 | Ntn Corporation | Tapered roller bearing |
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JP2007187308A (en) | 2005-12-16 | 2007-07-26 | Ntn Corp | Bearing device for wheel |
JP2008309270A (en) | 2007-06-15 | 2008-12-25 | Ntn Corp | Tapered roller bearing |
JP2016200227A (en) | 2015-04-10 | 2016-12-01 | Ntn株式会社 | Conical roller bearing |
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