JP2006349015A - Tapered roller bearing and method of designing the same - Google Patents

Tapered roller bearing and method of designing the same Download PDF

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JP2006349015A
JP2006349015A JP2005174502A JP2005174502A JP2006349015A JP 2006349015 A JP2006349015 A JP 2006349015A JP 2005174502 A JP2005174502 A JP 2005174502A JP 2005174502 A JP2005174502 A JP 2005174502A JP 2006349015 A JP2006349015 A JP 2006349015A
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face
tapered
ratio
roller
tapered roller
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Hiroki Fujiwara
宏樹 藤原
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NTN Corp
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NTN Toyo Bearing Co Ltd
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C19/00—Bearings with rolling contact, for exclusively rotary movement
    • F16C19/22—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings
    • F16C19/34—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load
    • F16C19/36—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load with a single row of rollers
    • F16C19/364—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load with a single row of rollers with tapered rollers, i.e. rollers having essentially the shape of a truncated cone
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • 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
    • F16C19/225—Details of the ribs supporting the end 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
    • F16C33/34—Rollers; Needles
    • F16C33/36—Rollers; Needles with bearing-surfaces other than cylindrical, e.g. tapered; with grooves in the bearing surfaces
    • F16C33/366—Tapered rollers, i.e. rollers generally shaped as truncated cones
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C2240/00—Specified values or numerical ranges of parameters; Relations between them
    • F16C2240/40—Linear dimensions, e.g. length, radius, thickness, gap
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C2240/00—Specified values or numerical ranges of parameters; Relations between them
    • F16C2240/40—Linear dimensions, e.g. length, radius, thickness, gap
    • F16C2240/70—Diameters; Radii

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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 capable of providing excellent anti-seizure property by maximizing a minimum oil film thickness at a contact part between the large end face of rollers and the large flange of an inner ring and suppressing roller manufacturing cost. <P>SOLUTION: This tapered roller bearing is so formed that the large end face 4a of the tapered rollers 4 is formed in a spherical surface and the side face 2ba of the large flange 2b of the inner ring 2 on the tapered roller 4 side is formed in a roughly tapered surface. A roller end face R ratio is set according to the ratio P/C of a dynamic equivalent radial load P to a basic dynamic rated load C as follows. When the tapered roller bearing is used in the range of P/C≤8%, the roller end face R ratio is set to 90.5 to 93%. When it is used in the range of 8%<P/C≤40%, the roller end face R ratio is set to 89 to 90.5. When it is used in the range of P/C>40%, the roller end face R ratio is set to 85 to 89%. When a distance between the tip point A of the tapered surface of the inner ring 2 forming a raceway track surface and a contact point B between the large end face 4a and the large flange 2b of the tapered rollers 4 is r<SB>b</SB>and a radius of curvature of the large end face 4a of the tapered rollers 4 is r<SB>m</SB>, the roller end face R ratio is indicated by R=r<SB>m</SB>/r<SB>b</SB>. <P>COPYRIGHT: (C)2007,JPO&INPIT

Description

この発明は、自動車のトランスミッション等に使用される円すいころ軸受、およびその設計方法に関する。   The present invention relates to a tapered roller bearing used for an automobile transmission and the like, and a design method thereof.

円すいころ軸受は、通常、その内輪の背面側に大鍔を有する。この大鍔の円すいころ側の側面は略円すい面とされており、球面の一部で構成されるころ大端面と接触する。この内輪大鍔ところ大端面との接触部では、相対運動にすべりを伴うため、高荷重で使用される自動車トランスミッション用の円すいころ軸受では油膜が薄くなり金属接触を発生する可能性がある。
従来、円すいころ軸受の大鍔部の潤滑性向上のための技術として、大鍔に周方向溝を形成することで金属接触を防止する方法（例えば特許文献１）、ころ大端面にランダムな研削痕を設け、この研削痕の谷部に潤滑油を溜める方法（例えば特許文献２）、ころ大端面に微小くぼみを点在させて、そのくぼみ内に潤滑油を溜める方法（例えば特許文献３）、ころ大端面と内輪大鍔の接触部におけるいずれか一方の接触面に自己潤滑性のある皮膜をコーティングする方法（例えば特許文献４）、ころ大端面と内輪大鍔の接触部におけるいずれか一方の接触面にセラミック皮膜をコーティングする方法（例えば特許文献５）などが提案されている。 Tapered roller bearings usually have a large collar on the back side of the inner ring. The side surface of this large bowl on the tapered roller side is a substantially conical surface, and comes into contact with the roller large end surface constituted by a part of a spherical surface. At the contact portion with the large end surface of the inner ring, the relative motion is accompanied by a slip, so that in a tapered roller bearing for an automobile transmission used at a high load, the oil film becomes thin and metal contact may occur.
Conventionally, as a technique for improving the lubricity of a large collar portion of a tapered roller bearing, a method of preventing metal contact by forming a circumferential groove in the large collar (for example, Patent Document 1), random grinding on a roller large end face A method of providing a trace and storing lubricating oil in a valley portion of the grinding mark (for example, Patent Document 2), a method of dispersing minute recesses on the roller large end surface, and storing the lubricant in the recess (for example, Patent Document 3) A method of coating a self-lubricating film on any one contact surface at the contact portion between the roller large end surface and the inner ring collar (for example, Patent Document 4), either one at the contact portion between the roller large end surface and the inner ring collar A method of coating a contact surface with a ceramic film (for example, Patent Document 5) has been proposed.

潤滑性向上の方法としては、このほか油膜の形成能を向上させることも考えられる。油膜の形成能を支配する要因の一つとして、ころ大端面の曲率半径がある。ころ大端面と内輪大鍔との接触点では、内輪大鍔面の曲率半径に対して、ころ大端面の曲率半径はやや小さく製作される。具体的には、内輪の軌道面となる円すい面の頂点から前記接触点までの距離をｒb とし、ころ大端面の曲率半径をｒm としたとき、ｒm ／ｒb ＝０．８〜０．９７程度である。ここで、Ｒ＝ｒm ／ｒb はころ端面Ｒ比と呼ばれる値である。このころ端面Ｒ比に関する従来技術として、特許文献６〜特許文献８などが知られている。
特開２００５−２４０２９号公報 特開２００３−２６９４６８号公報 特開平１０−１１０７３３号公報 特開平９−２８７６１６号公報 特開平９−１７７７７４号公報 特開２００２−２１３４５６号公報 特開２０００−１７０７７４号公報 実開平０５−０８７３３０号公報 As a method for improving the lubricity, it is also conceivable to improve the oil film forming ability. One of the factors governing the ability to form an oil film is the radius of curvature of the roller's large end face. At the contact point between the roller large end face and the inner ring large collar, the radius of curvature of the roller large end face is made slightly smaller than the radius of curvature of the inner ring large collar surface. Specifically, the distance from the apex of the conical surface of the inner ring raceway surface to the contact point and r b, rollers and a radius of curvature of the large end face and the r m, r m / r b = 0.8~ About 0.97. Here, R = r m / r b is a value called roller end R ratio. Patent Documents 6 to 8 are known as conventional techniques related to the roller end face R ratio.
JP-A-2005-24029 JP 2003-269468 A JP-A-10-110733 JP-A-9-287616 JP-A-9-177774 JP 2002-213456 A JP 2000-170774 A Japanese Utility Model Publication No. 05-087330

しかし、特許文献１〜５に開示される潤滑性向上の方法は、特殊な加工工程を要するため、製造コストが増大する。
また、特許文献６〜８に開示されるころ端面Ｒ比の設計技術では、使用条件にかかわらず、一律にころ端面Ｒ比を与えており、必ずしも最適値とは言いがたい。ころ端面Ｒ比の最適値は、耐焼付き性、油膜形成性、回転中のころの姿勢の安定性、加工性などによって検討されるべきであり、使用条件によって最適値は異なる。 However, the lubricity improving methods disclosed in Patent Documents 1 to 5 require a special processing step, which increases the manufacturing cost.
Further, in the roller end face R ratio design techniques disclosed in Patent Documents 6 to 8, the roller end face R ratio is uniformly given regardless of the use conditions, and is not necessarily an optimum value. The optimum value of the roller end face R ratio should be examined based on seizure resistance, oil film formation, stability of the posture of the rotating roller, workability, and the like, and the optimum value varies depending on use conditions.

この発明の目的は、使用条件に対して最適なころ端面Ｒ比とすることで、ころ大端面と内輪大鍔との接触部における最小油膜厚さを最大とでき、公差内では極端な油膜厚さの低下がなく、耐焼付き性に優れ、かつころの製造コストをできるだけ低く抑えることができる円すいころ軸受、およびその設計方法を提供することである。   An object of the present invention is to make the minimum oil film thickness at the contact portion between the roller large end face and the inner ring large collar by maximizing the roller end face R ratio with respect to the use conditions, and an extreme oil film thickness within the tolerance. It is an object of the present invention to provide a tapered roller bearing that is excellent in seizure resistance and that can keep the manufacturing cost of rollers as low as possible, and a design method thereof.

この発明の円すいころ軸受は、円すいころの大端面が球面、内輪の大鍔の円すいころ側の側面が略円すい面である円すいころ軸受であって、内輪の軌道面となる円すい面の頂点から、円すいころの大端面と上記大鍔との接触点までの距離をｒb 、円すいころの大端面の曲率半径をｒm としたときに、次式、
Ｒ＝ｒm ／ｒb
で示されるＲの値であるころ端面Ｒ比を、基本動定格荷重Ｃに対する動等価ラジアル荷重Ｐの割合Ｐ／Ｃが、
Ｐ／Ｃ≦８％の範囲で使用される軸受の場合には９０．５〜９３％とし、
８％＜Ｐ／Ｃ≦４０％で使用される軸受の場合には８９〜９０．５％とし、
Ｐ／Ｃ＞４０％の範囲で使用される軸受の場合には８５〜８９％、
としたことを特徴とする。 The tapered roller bearing according to the present invention is a tapered roller bearing in which the tapered roller has a large end surface that is a spherical surface, and a side surface on the tapered roller side of the inner ring is a tapered surface. , the distance to the contact point between the large end face and the large rib of the tapered rollers r b, the radius of curvature of the large end faces of tapered rollers is taken as r m, the following equation,
R = r m / r b
The ratio R / R of the roller end face, which is the value of R indicated by
In the case of a bearing used in the range of P / C ≦ 8%, the range is 90.5 to 93%.
In the case of a bearing used with 8% <P / C ≦ 40%, 89 to 90.5%,
85 to 89% for bearings used in the range of P / C> 40%,
It is characterized by that.

この構成によると、ＥＨＬ（elastohydrodynamic lubrication）理論、つまり弾性流体潤滑理論に基づく計算結果から、円すいころの大端面と内輪の大鍔の接触部での最小油膜厚さを最大にできる。そのため、公差内で極端な油膜厚さの低下がなく、内輪大鍔での耐焼付き性を向上させることができる。また、円すいころ軸受用の円すいころを大量生産する場合、ころ端面Ｒ比が１に近いほど低いコストで高精度に製作できるが、この発明によると、使用条件に応じて、ころ端面Ｒ比をできるだけ大きくするため、円すいころの製造コストをできるだけ低く抑えて高精度に製作できる。   According to this configuration, the minimum oil film thickness at the contact portion between the large end face of the tapered roller and the large collar of the inner ring can be maximized from the calculation result based on EHL (elastohydrodynamic lubrication) theory, that is, elastohydrodynamic lubrication theory. Therefore, there is no drastic reduction in the oil film thickness within the tolerance, and the seizure resistance in the inner ring can be improved. In addition, when mass producing tapered rollers for tapered roller bearings, the roller end surface R ratio can be manufactured with high accuracy at a lower cost as the roller end surface R ratio is closer to 1, but according to the present invention, the roller end surface R ratio can be increased depending on the use conditions. In order to make it as large as possible, it is possible to manufacture with high accuracy while keeping the manufacturing cost of tapered rollers as low as possible.

この発明の円すいころ軸受の設計方法は、円すいころの大端面が球面、内輪の大鍔の円すいころ側の側面が略円すい面である円すいころ軸受の設計方法であって、基本動定格荷重Ｃに対する動等価ラジアル荷重Ｐの割合Ｐ／Ｃと、内輪の軌道面となる円すい面の頂点から、円すいころの大端面と上記大鍔との接触点までの距離をｒb 、円すいころの大端面の曲率半径をｒm としたときに、次式、
Ｒ＝ｒm ／ｒb
で示されるＲの値であるころ端面Ｒ比との関係につき、
Ｐ／Ｃ≦８％の軸受では、ころ端面Ｒ比を呼び値９０．５〜９３％、
８％＜Ｐ／Ｃ≦４０％の軸受では、ころ端面Ｒ比を呼び値８９〜９０．５％、
Ｐ／Ｃ＞４０％の軸受では、ころ端面Ｒ比を呼び値８５〜８９％とし、
これら各呼び値の範囲を、対応するＰ／Ｃの円すいころ軸受におけるころ端面Ｒ比の許容最大値とする方法である。
この構成によると、ＥＨＬ理論に基づく計算結果から、最小油膜厚さを最大とすることができ、また公差範囲をころ端面Ｒ比が小さい方に与えることで耐焼付き性を向上させることができる。さらに、円すいころの姿勢安定性が向上し、かつ高精度の円すいころを低コストで製作できる。 The tapered roller bearing design method of the present invention is a tapered roller bearing design method in which the large end surface of the tapered roller is a spherical surface and the side surface on the tapered roller side of the inner ring of the inner ring is a substantially tapered surface, and the basic dynamic load rating C The ratio P / C of the dynamic equivalent radial load P with respect to, and the distance from the apex of the conical surface which is the raceway surface of the inner ring to the contact point between the large end surface of the tapered roller and the large flange, r b , the large end surface of the tapered roller the radius of curvature when the r m of the following formula,
R = r m / r b
With respect to the relationship with the roller end face R ratio, which is the value of R indicated by
For bearings with P / C ≦ 8%, the roller end face R ratio is a nominal value of 90.5 to 93%,
For bearings of 8% <P / C ≦ 40%, the roller end face R ratio is nominal value 89-90.5%,
For bearings with P / C> 40%, the roller end face R ratio is 85 to 89% nominal,
This is a method in which the range of each nominal value is the maximum allowable value of the roller end face R ratio in the corresponding tapered roller bearing of P / C.
According to this configuration, from the calculation result based on the EHL theory, the minimum oil film thickness can be maximized, and the seizure resistance can be improved by giving the tolerance range to the smaller roller end face R ratio. Further, the posture stability of the tapered roller is improved, and a highly accurate tapered roller can be manufactured at a low cost.

この発明の円すいころ軸受は、ころ端面Ｒ比を、Ｐ／ＣがＰ／Ｃ≦８％の範囲で使用される軸受の場合には９０．５〜９３とし、Ｐ／Ｃが８％＜Ｐ／Ｃ≦４０％で使用される軸受の場合には８９〜９０．５％とし、Ｐ／ＣがＰ／Ｃ＞４０％の範囲で使用されるの場合には８５〜８９％としたため、円すいころの大端面と内輪の大鍔の接触部での最小油膜厚さを最大にできて、公差内で極端な油膜厚さの低下がなく、内輪大鍔での耐焼付き性を向上させることができる。しかも、使用条件に対してころ端面Ｒ比を１にできるだけ近い値とするため、円すいころの製造コストをできるだけ低く抑えて高精度に製作できる。   In the tapered roller bearing according to the present invention, the roller end face R ratio is 90.5 to 93 when P / C is used in the range of P / C ≦ 8%, and P / C is 8% <P. For bearings used at / C ≦ 40%, it is 89-90.5%. When P / C is used in the range of P / C> 40%, it is 85-89%. The minimum oil film thickness at the contact area between the roller's large end face and the inner ring's large collar can be maximized, and there is no drastic reduction in oil film thickness within tolerances, improving seizure resistance on the inner ring's large collar. it can. In addition, since the roller end face R ratio is as close to 1 as possible with respect to the use conditions, it is possible to manufacture the tapered rollers with high accuracy while keeping the manufacturing cost of the tapered rollers as low as possible.

この発明の円すいころ軸受の設計方法は、基本動定格荷重Ｃに対する動等価ラジアル荷重Ｐの割合Ｐ／Ｃと、ころ端面Ｒ比との関係につき、
Ｐ／Ｃ≦８％の軸受では、ころ端面Ｒ比を呼び値９０．５〜９３％、
８％＜Ｐ／Ｃ≦４０％の軸受では、ころ端面Ｒ比を呼び値８９〜９０．５％、
Ｐ／Ｃ＞４０％の軸受では、ころ端面Ｒ比を呼び値８５〜８９％とし、
これら各呼び値の範囲を、対応するＰ／Ｃの円すいころ軸受におけるころ端面Ｒ比の許容最大値とするため、円すいころの大端面と内輪の大鍔の接触部での最小油膜厚さを最大にでき、公差内で極端な油膜厚さの低下がなく、内輪大鍔での耐焼付き性を向上させることができる。しかも、円すいころの製造コストをできるだけ低く抑えながら高精度に製作できる。 The tapered roller bearing design method of the present invention relates to the relationship between the ratio P / C of the dynamic equivalent radial load P to the basic dynamic load rating C and the roller end face R ratio.
For bearings with P / C ≦ 8%, the roller end face R ratio is a nominal value of 90.5 to 93%,
For bearings of 8% <P / C ≦ 40%, the roller end face R ratio is nominal value 89-90.5%,
For bearings with P / C> 40%, the roller end face R ratio is 85 to 89% nominal,
In order to set the range of each nominal value to the maximum allowable value of the roller end face R ratio in the corresponding P / C tapered roller bearing, the minimum oil film thickness at the contact portion between the large end face of the tapered roller and the large ring of the inner ring is maximized. It is possible to improve the seizure resistance in the inner ring large punch without causing an extreme decrease in the oil film thickness within the tolerance. Moreover, it can be manufactured with high accuracy while keeping the manufacturing cost of tapered rollers as low as possible.

この発明の一実施形態を図１ないし図５と共に説明する。この実施形態の円すいころ軸受１は、図１（Ａ）に断面図で示すように、内輪２と、外輪３と、これら内外輪２，３間に介在した円すいころ４とを有し、内外輪２，３間に軸方向の予圧を付与可能とした単列の円すいころ軸受である。内輪２は、外径面に円すい面とされた軌道面２ａを有し、外径の大径側および小径側に大鍔２ｂおよび小鍔２ｃをそれぞれ有する。外輪３は、内輪２の軌道面２ａに対向する内径面に円すい面とされた軌道面３ａを有する。上記両軌道面２ａ，３ａ間に複数個の円すいころ４が転動自在に介在している。これら円すいころ４は、保持器５により円周方向に所定間隔を隔てて保持されている。   An embodiment of the present invention will be described with reference to FIGS. The tapered roller bearing 1 of this embodiment has an inner ring 2, an outer ring 3, and a tapered roller 4 interposed between the inner and outer rings 2 and 3, as shown in a sectional view in FIG. This is a single row tapered roller bearing capable of applying an axial preload between the rings 2 and 3. The inner ring 2 has a raceway surface 2a which is a conical surface on the outer diameter surface, and a large collar 2b and a small collar 2c on the large diameter side and the small diameter side of the outer diameter, respectively. The outer ring 3 has a raceway surface 3 a which is a conical surface on the inner diameter surface facing the raceway surface 2 a of the inner ring 2. A plurality of tapered rollers 4 are interposed between the raceway surfaces 2a and 3a so as to freely roll. These tapered rollers 4 are held by a cage 5 at a predetermined interval in the circumferential direction.

円すいころ４の大端面４ａは球面とされ、内輪２の大鍔２ｂの円すいころ４側の側面である内輪大鍔面２ｂａ（図１（Ｂ））は、略円すい面とされている。内輪２の軌道面２ａである円すい面の頂点Ａから、円すいころ４の大端面４ａと内輪大鍔２ｂとの接触点Ｂまでの距離をｒb 、円すいころ４の大端面４ａの曲率半径をｒm としたときに、次式、
Ｒ＝ｒm ／ｒb
で示されるＲの値を、ころ端面Ｒ比と呼ぶ。 The large end surface 4a of the tapered roller 4 is a spherical surface, and the inner ring large collar surface 2ba (FIG. 1B) which is the side surface of the large collar 2b of the inner ring 2 on the tapered roller 4 side is a substantially tapered surface. The distance from the apex A of the tapered surface which is the raceway surface 2a of the inner ring 2 to the contact point B between the large end surface 4a of the tapered roller 4 and the inner ring large collar 2b is r b , and the curvature radius of the large end surface 4a of the tapered roller 4 is When r m ,
R = r m / r b
The value of R indicated by is called the roller end face R ratio.

この実施形態は、基本動定格荷重Ｃに対する動等価ラジアル荷重Ｐの割合Ｐ／Ｃと、ころ端面Ｒ比との関係につき、
Ｐ／Ｃ≦８％の範囲で使用される軸受ではころ端面Ｒ比を９０．５〜９３％とし、
８％＜Ｐ／Ｃ≦４０％で使用される軸受ではころ端面Ｒ比を８９〜９０．５％とし、
Ｐ／Ｃ＞４０％の範囲で使用される軸受ではころ端面Ｒ比を８５〜８９％、
としたものである。 This embodiment relates to the relationship between the ratio P / C of the dynamic equivalent radial load P to the basic dynamic load rating C and the roller end face R ratio.
For bearings used in the range of P / C ≦ 8%, the roller end face R ratio is 90.5 to 93%,
For bearings used with 8% <P / C ≦ 40%, the roller end face R ratio is 89-90.5%,
For bearings used in the range of P / C> 40%, the roller end face R ratio is 85 to 89%,
It is what.

この実施形態における円すいころ軸受１のように、円すいころ４の大端面４ａを球面、内輪大鍔２ｂの側面２ｂａを略円すい面とした円すいころ軸受おいて、円すいころ４を大量生産する場合、上記ころ端面Ｒ比が１に近いほど低コストで高精度に製作できる。
また、この円すいころ軸受１の運転中に円すいころ４がスキューした場合、ころ大端面４ａ上の接触点Ｂは正規の位置から摺動方向に移動する。これによってスキューを矯正しようとする力のモーメントが発生するが、ころ端面Ｒ比が大きいほど、小さなスキュー角で大きなモーメントが発生する。したがって円すいころ４の姿勢の安定性の観点からは、ころ端面Ｒ比は大きいほうが望ましい。 When the tapered roller 4 is mass-produced in a tapered roller bearing in which the large end surface 4a of the tapered roller 4 is a spherical surface and the side surface 2ba of the inner ring large collar 2b is a substantially tapered surface like the tapered roller bearing 1 in this embodiment, As the roller end face R ratio is closer to 1, it can be manufactured with higher accuracy at lower cost.
Further, when the tapered roller 4 is skewed during the operation of the tapered roller bearing 1, the contact point B on the roller large end surface 4a moves from the normal position in the sliding direction. As a result, a moment of force for correcting the skew is generated, but as the roller end face R ratio is larger, a larger moment is generated with a smaller skew angle. Therefore, from the viewpoint of the stability of the posture of the tapered roller 4, it is desirable that the roller end face R ratio is large.

一方、ころ端面Ｒ比が大きいほど、前記接触点Ｂでの接触楕円が大きくなる。接触楕円の長軸半径は内輪大鍔２ｂの周方向に存在する。円すいころ４がスキューし接触点Ｂが移動したとき、ころ端面Ｒ比が大きいほど接触楕円はころ大端面４ａと内輪大鍔面２ｂａの接触可能な領域からはみ出し易くなる。接触楕円がはみ出すと、エッジ部で過大な圧力が発生し、焼付きが生じる原因となる。焼付きが生じるとき、ころ大端面４ａと内輪大鍔面２ｂａの間には油膜が形成されておらず、金属接触状態となっている。このとき、円すいころ４には内輪大鍔面２ｂａとの摩擦によってスキューが生じる。   On the other hand, the larger the roller end face R ratio, the larger the contact ellipse at the contact point B. The major axis radius of the contact ellipse exists in the circumferential direction of the inner ring collar 2b. When the tapered roller 4 is skewed and the contact point B is moved, the larger the roller end surface R ratio, the easier the contact ellipse protrudes from the contactable region between the roller large end surface 4a and the inner ring large collar surface 2ba. When the contact ellipse protrudes, an excessive pressure is generated at the edge portion, which causes seizure. When seizure occurs, an oil film is not formed between the roller large end surface 4a and the inner ring large collar surface 2ba, and is in a metal contact state. At this time, the tapered roller 4 is skewed by friction with the inner ring large collar surface 2ba.

スキューによる接触点Ｂの移動量は、詳細な理論検討結果によれば、軌道面２ａの影響をほとんど受けず、鍔部での力のモーメントの釣り合いによって決定される。すなわち、次式の鍔荷重と摩擦力のころ重心まわりのモーメントの釣り合いである。
Ｑｄ＝μＱｌ
Ｑ：鍔荷重 ｄ：接触点Ｂの周方向移動量
μ：摩擦係数
ｌ：接触点Ｂところ重心の距離 The amount of movement of the contact point B due to the skew is determined by the balance of the moments of force at the buttocks according to the detailed theoretical examination results, with little influence of the track surface 2a. That is, it is a balance of moments around the center of gravity of the roller between the load of the following formula and the frictional force.
Qd = μQl
Q: Hail load d: Travel distance in the circumferential direction of contact point B μ: Friction coefficient l: Distance of the center of gravity at contact point B

接触楕円の大きさはＨertzの式によって計算できる。ここから、接触楕円がはみ出さない限界の荷重が求められ、例えば図２に示すグラフのようになる。このグラフから、ころ端面Ｒ比が小さいほど、耐焼付き性が良いことが分かる。   The size of the contact ellipse can be calculated by the Hertz equation. From this, a limit load that does not allow the contact ellipse to protrude is obtained, for example, as shown in the graph of FIG. From this graph, it can be seen that the smaller the roller end face R ratio, the better the seizure resistance.

焼付くためには金属接触を生じる必要があるが、油膜が厚ければ金属接触は生じ難い。このことから、同一の運転条件で最小油膜厚さが最大となるころ端面Ｒ比を与えることが、耐焼付き性向上の一手段となることが分かる。そこで、ころ大端面４ａと内輪大鍔面２ｂａの潤滑状態について、ＥＨＬ理論に基づいて計算したところ、図３〜図６にグラフで示す結果が得られた。
すなわち、図３や図４のグラフによると、回転速度や潤滑粘度をパラメータとして変化させても、最小油膜厚さを最大とするころ端面Ｒ比はほとんど変化しない。ところが、図５のグラフによると、鍔荷重をパラメータとして変化させると、最小油膜厚さを最大とするころ端面Ｒ比が変化し、鍔荷重が大きくなるほど、ころ端面Ｒ比の最適値が小さくなっている。また、最適値より小さいころ端面Ｒ比では、最小油膜厚さの減少はわずかであるが、最適値より大きいころ端面Ｒ比では、最小油膜厚さは急激に減少する。なお、図５のグラフにおいて、Ｐ／Ｃは、基本動定格荷重Ｃに対する動等価ラジアル荷重Ｐの割合を表す。 In order to seize, it is necessary to make metal contact. However, if the oil film is thick, metal contact is difficult to occur. From this, it can be seen that providing a roller end face R ratio that maximizes the minimum oil film thickness under the same operating conditions is one means of improving seizure resistance. Accordingly, the lubrication state of the roller large end face 4a and the inner ring large collar face 2ba was calculated based on the EHL theory, and the results shown in the graphs of FIGS. 3 to 6 were obtained.
That is, according to the graphs of FIGS. 3 and 4, even when the rotational speed and the lubricating viscosity are changed as parameters, the roller end face R ratio that maximizes the minimum oil film thickness hardly changes. However, according to the graph of FIG. 5, when the heel load is changed as a parameter, the roller end face R ratio that maximizes the minimum oil film thickness changes, and the optimum value of the roller end face R ratio decreases as the heel load increases. ing. Further, when the roller end face R ratio is smaller than the optimum value, the minimum oil film thickness decreases slightly, but when the roller end face R ratio is larger than the optimum value, the minimum oil film thickness decreases rapidly. In the graph of FIG. 5, P / C represents the ratio of the dynamic equivalent radial load P to the basic dynamic load rating C.

以上の計算結果によると、油膜の形成性にとって最適なころ端面Ｒ比は荷重に依存し、円すいころ軸受１の設計において、鍔荷重が小さいときはころ端面Ｒ比を大きくし、鍔荷重が大きいときはころ端面Ｒ比を小さくすれば良いことが分かる。また、製造上、ころ端面Ｒ比には公差を与える必要があるが、上記計算結果によれば最適値以下を公差範囲に設定しなければならないことが分かる。   According to the above calculation results, the optimum roller end face R ratio for oil film formation depends on the load. In the design of the tapered roller bearing 1, when the kite load is small, the roller end surface R ratio is increased and the kite load is large. Sometimes it can be seen that the roller end face R ratio should be reduced. Further, in manufacturing, it is necessary to give a tolerance to the roller end face R ratio, but according to the above calculation result, it can be seen that the tolerance value must be set to the optimum value or less.

図５は、Ｐ／Ｃと最適ころ端面Ｒ比の関係を示したグラフである。同図によれば、
Ｐ／Ｃ≦８％の軸受では、ころ端面Ｒ比を９０．５〜９３％とし、
８％＜Ｐ／Ｃ≦４０％の軸受では、ころ端面Ｒ比を８９〜９０．５％とし、
Ｐ／Ｃ＞４０％の軸受では、ころ端面Ｒ比を８５〜８９％とすれば良いことが分かる。 FIG. 5 is a graph showing the relationship between P / C and the optimum roller end face R ratio. According to the figure,
For bearings with P / C ≦ 8%, the roller end face R ratio is 90.5 to 93%,
For a bearing of 8% <P / C ≦ 40%, the roller end face R ratio is 89-90.5%,
It can be seen that for a bearing with P / C> 40%, the roller end face R ratio should be 85-89%.

円すいころ軸受１が自動車トランスミッション用の場合には、最大荷重が作用する条件で、Ｐ／Ｃはおよそ３０％である。この場合、図５のグラフのように、ころ端面Ｒ比を９０％とすることで最小油膜厚さを最大とすることができ、また公差範囲をころ端面Ｒ比が小さい方に与えることで耐焼付き性を向上させることができる。   When the tapered roller bearing 1 is for an automobile transmission, P / C is approximately 30% under the condition that the maximum load is applied. In this case, as shown in the graph of FIG. 5, the minimum oil film thickness can be maximized by setting the roller end face R ratio to 90%, and the tolerance range is given to the smaller roller end face R ratio so Adhesiveness can be improved.

上記した設計手法は、自動車トランスミッション用円すいころ軸受に限定されるものではない。例えば、工作機械主軸用軸受では、予圧によってＰ／Ｃ＝６％程度の荷重が作用している。このとき、最小油膜厚さが最大となるころ端面Ｒ比は、図５のグラフから、９２％とすれば良いことが分かる。すなわち、ころ端面Ｒ比を一律に８５％とせず最適値を与えることで、ころ端面Ｒ比が大きくなり、円すいころ４の姿勢安定性が向上し、かつ高精度の円すいころ４を低コストで製作できる。   The design method described above is not limited to tapered roller bearings for automobile transmissions. For example, in a machine tool spindle bearing, a load of about P / C = 6% is applied by preload. At this time, it can be seen from the graph of FIG. 5 that the roller end surface R ratio with the minimum minimum oil film thickness is 92%. That is, the roller end surface R ratio is not uniformly set to 85%, and the optimum value is given, so that the roller end surface R ratio is increased, the posture stability of the tapered roller 4 is improved, and the highly accurate tapered roller 4 is manufactured at low cost. Can be produced.

このように、この実施形態では、基本動定格荷重Ｃに対する動等価ラジアル荷重Ｐの割合Ｐ／Ｃが、Ｐ／Ｃ≦８％の範囲で使用される軸受の場合にはころ端面Ｒ比を９０．５〜９３％とし、８％＜Ｐ／Ｃ≦４０％で使用される軸受の場合にはころ端面Ｒ比を８９〜９０．５％とし、Ｐ／Ｃ＞４０％の範囲で使用される軸受の場合にはころ端面Ｒ比を８５〜８９％、としたため、ころ大端面４ａと内輪大鍔２ｂの接触部での最小油膜厚さが最大となり、公差内で極端な油膜厚さの低下がなくて、内輪大鍔２ｂでの耐焼付き性を向上させることができる。しかも、円すいころ４の製造コストをできるだけ低く抑えることができる。   Thus, in this embodiment, in the case of a bearing used in a range where the ratio P / C of the dynamic equivalent radial load P to the basic dynamic load rating C is P / C ≦ 8%, the roller end face R ratio is 90. In the case of a bearing used at 8% <P / C ≦ 40%, the roller end face R ratio is 89-90.5% and is used in the range of P / C> 40%. In the case of a bearing, since the roller end face R ratio is 85 to 89%, the minimum oil film thickness at the contact portion between the roller large end face 4a and the inner ring collar 2b is maximized, and the oil film thickness is extremely reduced within the tolerance. Therefore, the seizure resistance in the inner ring large collar 2b can be improved. Moreover, the manufacturing cost of the tapered roller 4 can be kept as low as possible.

円すいころ軸受の設計方法としては、上記のように荷重条件に応じて定めるころ端面Ｒ比の範囲を呼び値とし、呼び値の範囲を最大許容寸法とすることで、使用条件に対して最適なころ端面Ｒ比とすることができる。
すなわち、この設計方法は、
Ｐ／Ｃ≦８％の軸受では、ころ端面Ｒ比を呼び値９０．５〜９３％、
８％＜Ｐ／Ｃ≦４０％の軸受では、ころ端面Ｒ比を呼び値８９〜９０．５％、
Ｐ／Ｃ＞４０％の軸受では、ころ端面Ｒ比を呼び値８５〜８９％とし、
これら各呼び値の範囲を、対応するＰ／Ｃの円すいころ軸受におけるころ端面Ｒ比の許容最大値とする。
これにより、ころ大端面４ａと内輪大鍔２ｂの接触部での最小油膜厚さが最大となり、公差内で極端な油膜厚さの低下がなくて、内輪大鍔２ｂでの耐焼付き性を向上させることができる円すいころ軸受１の設計が行える。しかも、円すいころ４の製造コストをできるだけ低く抑えることができる。 As a tapered roller bearing design method, the roller end surface R ratio range determined according to the load conditions as described above is set as the nominal value, and the nominal value range is set to the maximum allowable dimension, so that the roller end surface most suitable for the usage conditions is obtained. R ratio can be used.
In other words, this design method
For bearings with P / C ≦ 8%, the roller end face R ratio is a nominal value of 90.5 to 93%,
For bearings of 8% <P / C ≦ 40%, the roller end face R ratio is nominal value 89-90.5%,
For bearings with P / C> 40%, the roller end face R ratio is 85 to 89% nominal,
The range of each nominal value is the allowable maximum value of the roller end face R ratio in the corresponding tapered roller bearing of P / C.
As a result, the minimum oil film thickness at the contact portion between the roller large end face 4a and the inner ring collar 2b is maximized, and there is no drastic decrease in oil film thickness within the tolerance, improving seizure resistance in the inner ring collar 2b. The tapered roller bearing 1 can be designed. Moreover, the manufacturing cost of the tapered rollers 4 can be kept as low as possible.

（Ａ）はこの発明の一実施形態にかかる円すいころ軸受の断面図、（Ｂ）は同円すいころ軸受の部分拡大断面図である。(A) is sectional drawing of the tapered roller bearing concerning one Embodiment of this invention, (B) is a partial expanded sectional view of the tapered roller bearing. 円すいころ軸受におけるころ端面Ｒ比と接触楕円がはみ出さない限界鍔荷重との関係を、摩擦係数をパラメータとして示すグラフである。It is a graph which shows the relationship between the roller end surface R ratio in a tapered roller bearing, and the limit reed load which a contact ellipse does not protrude, using a friction coefficient as a parameter. 円すいころ軸受におけるころ端面Ｒ比と最小油膜厚さとの関係を、回転速度をパラメータとして示すグラフである。It is a graph which shows the relationship between the roller end surface R ratio and the minimum oil film thickness in a tapered roller bearing, using a rotational speed as a parameter. 円すいころ軸受におけるころ端面Ｒ比と最小油膜厚さとの関係を、潤滑油粘度をパラメータとして示すグラフである。It is a graph which shows the relationship between the roller end surface R ratio and the minimum oil film thickness in a tapered roller bearing, using lubricating oil viscosity as a parameter. 円すいころ軸受におけるころ端面Ｒ比と最小油膜厚さとの関係を、鍔荷重をパラメータとして示すグラフである。It is a graph which shows the relationship between the roller end surface R ratio and minimum oil film thickness in a tapered roller bearing as a parameter | corrosion load. Ｐ／Ｃところ端面Ｒ比の関係を示すグラフである。It is a graph which shows the relationship of P / C place end surface R ratio.

符号の説明Explanation of symbols

２…内輪
２ａ…内輪軌道面（円すい面）
２ｂ…大鍔
２ｂａ…内輪大鍔面
４…円すいころ
４ａ…大端面
Ａ…内輪円すい面の頂点 Ｂ…大端面・大鍔の接触点 ｒb …頂点・接触点間の距離 ｒm …大端面の曲率半径 2 ... Inner ring 2a ... Inner ring raceway surface (conical surface)
2b ... large collar 2ba ... inner ring large collar surface 4: tapered roller 4a ... large end face A ... apex of inner ring conical surface B ... contact point between large end face and large collar r b ... distance between apex and contact point r m ... large end face Radius of curvature

Claims (4)

円すいころの大端面が球面、内輪の大鍔の円すいころ側の側面が略円すい面である円すいころ軸受であって、
基本動定格荷重Ｃに対する動等価ラジアル荷重Ｐの割合Ｐ／Ｃが、
Ｐ／Ｃ≦８％であり、
内輪の軌道面となる円すい面の頂点から、円すいころの大端面と上記大鍔との接触点までの距離をｒb 、円すいころの大端面の曲率半径をｒm としたときに、次式、
Ｒ＝ｒm ／ｒb
で示されるＲの値であるころ端面Ｒ比を９０．５〜９３％としたことを特徴とする円すいころ軸受。 A tapered roller bearing in which the large end surface of the tapered roller is a spherical surface, and the side surface on the tapered roller side of the collar of the inner ring is a substantially tapered surface,
The ratio P / C of the dynamic equivalent radial load P to the basic dynamic load rating C is
P / C ≦ 8%,
From the apex of conical surface as the inner ring raceway surface, the distance to the contact point between the large end face and the large rib of the tapered rollers r b, the radius of curvature of the large end faces of tapered rollers is taken as r m, the following formula ,
R = r m / r b
A tapered roller bearing having a roller end face R ratio of 90.5 to 93%, which is a value of R shown in FIG. 円すいころの大端面が球面、内輪の大鍔の円すいころ側の側面が略円すい面である円すいころ軸受であって、
基本動定格荷重Ｃに対する動等価ラジアル荷重Ｐの割合Ｐ／Ｃが、
８％＜Ｐ／Ｃ≦４０％であり、
内輪の軌道面となる円すい面の頂点から、円すいころの大端面と上記大鍔との接触点までの距離をｒb 、円すいころの大端面の曲率半径をｒm としたときに、次式、
Ｒ＝ｒm ／ｒb
で示されるＲの値であるころ端面Ｒ比を８９〜９０．５％としたことを特徴とする円すいころ軸受。 A tapered roller bearing in which the large end surface of the tapered roller is a spherical surface, and the side surface on the tapered roller side of the collar of the inner ring is a substantially tapered surface,
The ratio P / C of the dynamic equivalent radial load P to the basic dynamic load rating C is
8% <P / C ≦ 40%,
From the apex of conical surface as the inner ring raceway surface, the distance to the contact point between the large end face and the large rib of the tapered rollers r b, the radius of curvature of the large end faces of tapered rollers is taken as r m, the following formula ,
R = r m / r b
A tapered roller bearing having a roller end face R ratio of 89 to 90.5%, which is a value of R shown in FIG. 円すいころの大端面が球面、内輪の大鍔の円すいころ側の側面が略円すい面である円すいころ軸受であって、
基本動定格荷重Ｃに対する動等価ラジアル荷重Ｐの割合Ｐ／Ｃが、
Ｐ／Ｃ＞４０％であり、
内輪の軌道面となる円すい面の頂点から、円すいころの大端面と上記大鍔との接触点までの距離をｒb 、円すいころの大端面の曲率半径をｒm としたときに、次式、
Ｒ＝ｒm ／ｒb
で示されるＲの値であるころ端面Ｒ比を８５〜８９％としたことを特徴とする円すいころ軸受。 A tapered roller bearing in which the large end surface of the tapered roller is a spherical surface, and the side surface on the tapered roller side of the collar of the inner ring is a substantially tapered surface,
The ratio P / C of the dynamic equivalent radial load P to the basic dynamic load rating C is
P / C> 40%,
From the apex of conical surface as the inner ring raceway surface, the distance to the contact point between the large end face and the large rib of the tapered rollers r b, the radius of curvature of the large end faces of tapered rollers is taken as r m, the following formula ,
R = r m / r b
A tapered roller bearing having a roller end face R ratio of 85 to 89%, which is a value of R shown in FIG. 円すいころの大端面が球面、内輪の大鍔の円すいころ側の側面が略円すい面である円すいころ軸受の設計方法であって、
基本動定格荷重Ｃに対する動等価ラジアル荷重Ｐの割合Ｐ／Ｃと、
内輪の軌道面となる円すい面の頂点から、円すいころの大端面と上記大鍔との接触点までの距離をｒb 、円すいころの大端面の曲率半径をｒm としたときに、次式、
Ｒ＝ｒm ／ｒb
で示されるＲの値であるころ端面Ｒ比との関係につき、
Ｐ／Ｃ≦８％の軸受では、ころ端面Ｒ比を呼び値９０．５〜９３％、
８％＜Ｐ／Ｃ≦４０％の軸受では、ころ端面Ｒ比を呼び値８９〜９０．５％、
Ｐ／Ｃ＞４０％の軸受では、ころ端面Ｒ比を呼び値８５〜８９％とし、
これら各呼び値の範囲を、対応するＰ／Ｃの円すいころ軸受におけるころ端面Ｒ比の許容最大値とする、
円すいころ軸受の設計方法。 A tapered roller bearing design method in which the tapered roller has a large end surface that is a spherical surface, and a side surface on the tapered roller side of the inner ring is a tapered surface.
The ratio P / C of the dynamic equivalent radial load P to the basic dynamic load rating C,
From the apex of conical surface as the inner ring raceway surface, the distance to the contact point between the large end face and the large rib of the tapered rollers r b, the radius of curvature of the large end faces of tapered rollers is taken as r m, the following formula ,
R = r m / r b
With respect to the relationship with the roller end face R ratio, which is the value of R indicated by
For bearings with P / C ≦ 8%, the roller end face R ratio is a nominal value of 90.5 to 93%,
For bearings of 8% <P / C ≦ 40%, the roller end face R ratio is nominal value 89-90.5%,
For bearings with P / C> 40%, the roller end face R ratio is 85 to 89% nominal,
The range of each nominal value is the allowable maximum value of the roller end face R ratio in the corresponding tapered roller bearing of P / C.
Tapered roller bearing design method.
JP2005174502A 2005-06-15 2005-06-15 Tapered roller bearing and method of designing the same Pending JP2006349015A (en)

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Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102007019917A1 (en) * 2007-04-27 2008-10-30 Ab Skf Roller bearing with running tracks which widen out in taper from one end to other generally useful in mechanical bearing technology shows minimal wear on inclined surfaces on which rear faces of roller bearing run
JP2016038081A (en) * 2014-08-11 2016-03-22 株式会社ジェイテクト Tapered roller bearing

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102007019917A1 (en) * 2007-04-27 2008-10-30 Ab Skf Roller bearing with running tracks which widen out in taper from one end to other generally useful in mechanical bearing technology shows minimal wear on inclined surfaces on which rear faces of roller bearing run
DE102007019917B4 (en) * 2007-04-27 2009-04-09 Ab Skf Tapered roller bearings
JP2016038081A (en) * 2014-08-11 2016-03-22 株式会社ジェイテクト Tapered roller bearing

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