JP5233494B2 - Tapered roller bearings - Google Patents

Tapered roller bearings Download PDF

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JP5233494B2
JP5233494B2 JP2008204666A JP2008204666A JP5233494B2 JP 5233494 B2 JP5233494 B2 JP 5233494B2 JP 2008204666 A JP2008204666 A JP 2008204666A JP 2008204666 A JP2008204666 A JP 2008204666A JP 5233494 B2 JP5233494 B2 JP 5233494B2
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cage
inner ring
diameter side
tapered roller
claw portion
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JP2009264576A (en
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佳宏朗 佐藤
友章 坂瀬
雅人 谷口
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NSK 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
    • 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
    • F16C33/4605—Details of interaction of cage and race, e.g. retention or centring
    • 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
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/30—Parts of ball or roller bearings
    • F16C33/46—Cages for rollers or needles
    • F16C33/4617—Massive or moulded cages having cage pockets surrounding the rollers, e.g. machined window cages
    • F16C33/4623—Massive or moulded cages having cage pockets surrounding the rollers, e.g. machined window cages formed as one-piece cages, i.e. monoblock cages
    • F16C33/4635—Massive or moulded cages having cage pockets surrounding the rollers, e.g. machined window cages formed as one-piece cages, i.e. monoblock cages made from plastic, e.g. injection moulded window cages
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/30—Parts of ball or roller bearings
    • F16C33/46—Cages for rollers or needles
    • F16C33/54—Cages for rollers or needles made from wire, strips, or sheet metal
    • F16C33/542—Cages for rollers or needles made from wire, strips, or sheet metal made from sheet metal
    • F16C33/543—Cages for rollers or needles made from wire, strips, or sheet metal made from sheet metal from a single part

Description

本発明は、保持器を有する円錐ころ軸受に関する。   The present invention relates to a tapered roller bearing having a cage.

円錐ころ軸受は、一般に、内輪と、この内輪の外周面に形成された軌道面と対向する軌道面を有する外輪と、この外輪の軌道面と内輪の軌道面との間に設けられた複数の円錐ころと、これらの円錐ころを保持する保持器とを具備した構成となっている。
このような円錐ころ軸受は、図１９に示すように、保持器４に保持された円錐ころ３を内輪１及び外輪２の円周方向に案内するための鍔部５を内輪１の大径側端部に有しているとともに、円錐ころ３及び保持器４を内輪１に非分離で組み付けできるようにする目的で、鍔部５より高さの低い鍔部６を内輪１の小径側端部に有している場合が多い（例えば、特許文献１〜３参照）。また、内輪１に組み付けられる保持器４としては、鋼板をプレス成形してなるプレス成形保持器（例えば、特許文献４参照）や、樹脂を射出成形してなる樹脂製保持器（例えば、特許文献５参照）を用いている場合が多い。 The tapered roller bearing generally has an inner ring, an outer ring having a raceway surface opposed to a raceway surface formed on the outer peripheral surface of the inner ring, and a plurality of provided between the raceway surface of the outer ring and the raceway surface of the inner ring. It has a configuration comprising a tapered roller and a cage for holding these tapered rollers.
As shown in FIG. 19, such a tapered roller bearing has a flange 5 for guiding the tapered roller 3 held by the cage 4 in the circumferential direction of the inner ring 1 and the outer ring 2 on the large diameter side of the inner ring 1. In order to enable the tapered roller 3 and the retainer 4 to be assembled to the inner ring 1 in a non-separable manner, the flange 6 having a height lower than that of the flange 5 is provided on the small-diameter side end of the inner ring 1. (See, for example, Patent Documents 1 to 3). Further, as the cage 4 assembled to the inner ring 1, a press-molded cage formed by press-molding a steel plate (for example, see Patent Document 4) or a resin cage formed by injection-molding a resin (for example, Patent Document) 5) is often used.

しかし、保持器４がプレス成形保持器の場合には、円錐ころ３が保持された保持器４を内輪１に組み付けた後、保持器４の小径側端部を内輪側に加締めることによって、保持器４が内輪１から分離しないようにしている。このため、保持器４の小径側端部を内輪側に加締める工程を要し、コストの増大を招く。
一方、保持器４が樹脂製保持器の場合は、保持器の弾性変形を利用して、円錐ころ３を保持器４の保持器ポケット４ａに挿入（パチン挿入）できるため、保持器４の小径側端部を内輪側に加締める必要はないが、内輪１の小径側端部に鍔部６が設けられていないと、外輪２を挿入して保持器４と円錐ころ３の軸方向位置を固定しない限り、保持器４が内輪１の小径側に抜けてしまうおそれがある。 However, when the cage 4 is a press-molded cage, after assembling the cage 4 holding the tapered rollers 3 to the inner ring 1, by crimping the small diameter side end of the cage 4 to the inner ring side, The cage 4 is prevented from being separated from the inner ring 1. For this reason, the process which crimps the small diameter side edge part of the holder | retainer 4 to the inner ring | wheel side is required, and the increase in cost is caused.
On the other hand, when the retainer 4 is a resin retainer, the tapered roller 3 can be inserted into the retainer pocket 4a of the retainer 4 using the elastic deformation of the retainer. Although it is not necessary to crimp the side end portion to the inner ring side, if the flange portion 6 is not provided at the small diameter side end portion of the inner ring 1, the outer ring 2 is inserted and the axial positions of the cage 4 and the tapered roller 3 are set. Unless it is fixed, there is a possibility that the cage 4 will come out to the small diameter side of the inner ring 1.

そこで、内輪の小径側端部に鍔部を設けることなく円錐ころ及び保持器を内輪に非分離で組み付けできるようにした円錐ころ軸受として、保持器の大径側端部に爪部を設けたものが特許文献６に開示されている。
特開２００５−６９４２１号公報（段落００１４、図１） 特開２００５−１２１０９７号公報（段落０００２、図４） 特開２００６−３２９２６０号公報（図７） 特開２００４−２８２７０号公報 特開２００６−７０９２６号公報 特開２００５−９８４１２号公報 Therefore, as a tapered roller bearing in which the tapered roller and the cage can be assembled to the inner ring in a non-separable manner without providing a flange on the small diameter side end portion of the inner ring, a claw portion is provided on the large diameter side end portion of the cage. This is disclosed in Patent Document 6.
Japanese Patent Laying-Open No. 2005-69421 (paragraph 0014, FIG. 1) JP 2005-121097 A (paragraph 0002, FIG. 4) Japanese Patent Laying-Open No. 2006-329260 (FIG. 7) JP 2004-28270 A JP 2006-70926 A JP-A-2005-98412

しかしながら、特許文献６に示されたものでは、保持器が内輪の小径側に移動すると、爪部が内輪の大径側端部に設けた鍔部と干渉するため、その部分で摩耗が生じるという問題があった。また、円錐ころ軸受は潤滑剤が内輪の小径側から大径側に流れるポンピング作用を有し、内輪の小径側端部に鍔部が無いほうがポンピング作用は大きく、潤滑剤の流れは円滑となるが、特許文献６に示されたものでは、保持器が内輪の小径側に移動すると、保持器の大径側端部に設けた爪部が内輪の大径側端部に設けた逃げ凹部としての環状段部に接触するため、潤滑剤の流れが阻害されるという問題もあった。
そこで、本発明は上記の問題点に着目してなされたものであり、その目的は、潤滑剤の流れを阻害することを抑制し、低トルク化を実現した円錐ころ軸受を提供することにある。 However, in the one shown in Patent Document 6, when the cage moves to the small diameter side of the inner ring, the claw portion interferes with the flange portion provided at the large diameter side end portion of the inner ring, so that wear occurs at that portion. There was a problem. In addition, the tapered roller bearing has a pumping action in which the lubricant flows from the smaller diameter side to the larger diameter side of the inner ring, and the pumping action is greater when the inner ring has no flange on the smaller diameter side end, and the flow of the lubricant becomes smoother. However, in the one disclosed in Patent Document 6, when the cage moves to the small diameter side of the inner ring, the claw portion provided at the large diameter side end portion of the cage serves as a relief recess provided at the large diameter side end portion of the inner ring. There is also a problem that the flow of the lubricant is obstructed because of contact with the annular step.
Accordingly, the present invention has been made paying attention to the above-mentioned problems, and an object of the present invention is to provide a tapered roller bearing that suppresses the flow of the lubricant and realizes low torque. .

上記課題を解決するために、請求項１記載の発明に係る円錐ころ軸受は、内輪と、該内輪の外周面に形成された軌道面と対向する軌道面を有する外輪と、前記内輪の軌道面と前記外輪の軌道面との間に設けられた複数の円錐ころと、該円錐ころを収容保持する複数の保持器ポケットを有する保持器とを具備してなり、前記内輪の大径側端部に鍔部を有する円錐ころ軸受であって、前記鍔部に形成された逃げ凹部、又は内輪端面と所定の間隔を有して位置する爪部を、前記保持器の大径側端部に有し、前記内輪の軌道面が前記円錐ころの転動面に接触すると共に前記鍔部と前記円錐ころの端面に接触し、かつ前記保持器の中心軸が前記内輪の中心軸と一致するとき、前記爪部の内側面と、該内側面に対向する前記逃げ凹部、又は前記内輪の端面との間の軸方向隙間をａ、前記円錐ころにおいて前記逃げ凹部が設けられた側の端面と前記保持器ポケットとの間の軸方向隙間をｂ、前記爪部の外側面と前記逃げ凹部との間の軸方向隙間をｃ、前記円錐ころにおいて前記逃げ凹部が設けられた側と反対側の端面と前記保持器ポケットとの間の軸方向隙間をｄとしたとき、ａ＞ｂ、ｃ＞ｄとし、
前記内輪と前記保持器との間から軸受内に油が流入することを抑制するために、前記内輪の軌道面に対して所定の間隙を形成する突起部が、前記保持器の小径側端部に形成され、
前記内輪と前記保持器との間から軸受内に油が流入することを更に抑制するために、前記突起部が前記内輪の小径側端部の一部を覆うように形成され、
前記小径側から大径側への油の流れに抗って軸受内部への油の流入を低減するために、前記突起部の小径側の面は、回転軸に直交する方向に対して所定の角度で傾斜しており、
前記内輪大径方向に、前記爪部が逃げ凹部へ挿入しやすく、その逆方向には前記爪部が前記凹部から脱落し難い形状とし、
前記爪部は、大径側を傾斜させた楔形をなすと共に、小径側に湾曲した切り欠きが形成されたことを特徴とする。 In order to solve the above-mentioned problems, a tapered roller bearing according to the first aspect of the present invention includes an inner ring, an outer ring having a raceway surface facing a raceway surface formed on an outer peripheral surface of the inner ring, and a raceway surface of the inner ring. A plurality of tapered rollers provided between the outer ring and the raceway surface of the outer ring, and a cage having a plurality of cage pockets for receiving and holding the tapered rollers. A tapered roller bearing having a flange portion on the large-diameter side end portion of the cage having a relief recess formed in the flange portion or a claw portion located at a predetermined distance from the inner ring end face. And when the raceway surface of the inner ring contacts the rolling surface of the tapered roller and the end surface of the flange and the tapered roller, and the central axis of the cage coincides with the central axis of the inner ring, The inner surface of the claw portion, the relief recess facing the inner surface, or the end surface of the inner ring The axial clearance between the end of the tapered roller on the side where the relief recess is provided and the cage pocket is b, the outer surface of the claw portion and the relief recess A> b, c> d, where c is the axial clearance between them, and d is the axial clearance between the end face of the tapered roller opposite to the side where the relief recess is provided and the cage pocket. age,
In order to prevent oil from flowing into the bearing from between the inner ring and the cage, a protrusion that forms a predetermined gap with respect to the raceway surface of the inner ring is a small diameter side end of the cage. It is formed on,
In order to further suppress the oil from flowing into the bearing from between the inner ring and the cage, the protrusion is formed so as to cover a part of the small diameter side end of the inner ring,
In order to reduce the inflow of oil into the bearing against the flow of oil from the small-diameter side to the large-diameter side, the surface on the small-diameter side of the protruding portion has a predetermined direction with respect to the direction orthogonal to the rotation axis. Inclined at an angle,
In the inner ring large-diameter direction, the claw portion is easy to insert into the escape recess, and in the opposite direction, the claw portion does not easily fall out of the recess,
The claw portion has a wedge shape in which the large diameter side is inclined, and a notch curved to the small diameter side is formed .

請求項２記載の発明に係る円錐ころ軸受は、請求項１に記載の円錐ころ軸受において、前記保持器が樹脂製保持器であることを特徴とする。 Tapered roller bearing according to the invention 請 Motomeko 2 wherein, in the tapered roller bearing according to claim 1, wherein said retainer is a resin cage.

本発明に係る円錐ころ軸受によれば、内輪の小径側端部に鍔部を設けたり、保持器の小径側端部を加締めたりする必要がないので、コストの低減を図ることができる。また、軸受の運転時には保持器が内輪の小径側に移動すると爪部の内側面が逃げ凹部の壁面部に接触する前に保持器が円錐ころの大径側端面に当接し、保持器が内輪の大径側に移動すると爪部の外側面が逃げ凹部の壁面部に接触する前に保持器が円錐ころの小径側端面に当接する。これにより、保持器が軸方向に移動しても爪部が内輪と接触することがないので、内輪や爪部に摩耗が生じたり、爪部が内輪に接触することによって潤滑剤の流れを阻害することを抑制し、低トルク化を実現することができる。   According to the tapered roller bearing according to the present invention, it is not necessary to provide a flange portion at the small diameter side end portion of the inner ring or to crimp the small diameter side end portion of the cage, so that the cost can be reduced. Also, when the cage is moved to the smaller diameter side of the inner ring during the operation of the bearing, the cage comes into contact with the larger diameter side end surface of the tapered roller before the inner surface of the claw portion comes into contact with the wall surface portion of the relief recess, and the cage When the outer diameter of the claw portion moves to the larger diameter side, the cage comes into contact with the smaller diameter side end surface of the tapered roller before the outer surface of the claw portion comes into contact with the wall surface portion of the recess. As a result, even if the cage moves in the axial direction, the claw portion does not come into contact with the inner ring, so that the inner ring or the claw portion is worn out or the claw portion comes into contact with the inner ring to obstruct the flow of the lubricant. It is possible to suppress the torque and realize a reduction in torque.

以下、本発明に係る円錐ころ軸受を図面に基づいて説明する。図１は本発明の第１の実施形態に係る円錐ころ軸受の断面図、図２は図１のＡ部を拡大して示す図、図３は図１に示す円錐ころ軸受の円錐ころと保持器との間の軸方向隙間を示す図であり、図１に示されるように、第１の実施形態に係る円錐ころ軸受は内輪１、外輪２、円錐ころ３及び保持器４を備えている。   Hereinafter, a tapered roller bearing according to the present invention will be described with reference to the drawings. 1 is a cross-sectional view of a tapered roller bearing according to a first embodiment of the present invention, FIG. 2 is an enlarged view of a portion A in FIG. 1, and FIG. 3 is a view showing a tapered roller and a holder of the tapered roller bearing shown in FIG. FIG. 1 is a view showing an axial gap between the inner ring 1, the outer ring 2, the tapered roller 3, and the cage 4, as shown in FIG. 1. .

内輪１は外輪２の内周面に形成された軌道面２ａと対向する軌道面１ａを外周面に有しており、この軌道面１ａと軌道面２ａとの間に、保持器４に保持された複数の円錐ころ３が内輪１及び外輪２の円周方向に転動自在に設けられている。
また、内輪１は保持器４に保持された円錐ころ３を内輪１及び外輪２の円周方向に案内するための鍔部５を大径側端部のみに有しており、この鍔部５の周面部には、逃げ凹部としての逃げ溝７（図２参照）が鍔部５の全周にわたって形成されている。 The inner ring 1 has a raceway surface 1a opposed to a raceway surface 2a formed on the inner circumference surface of the outer ring 2 on the outer circumference surface, and is held by a cage 4 between the raceway surface 1a and the raceway surface 2a. A plurality of tapered rollers 3 are provided so as to roll in the circumferential direction of the inner ring 1 and the outer ring 2.
Further, the inner ring 1 has a flange 5 for guiding the tapered roller 3 held by the cage 4 in the circumferential direction of the inner ring 1 and the outer ring 2 only at the end on the large diameter side. A clearance groove 7 (see FIG. 2) as a clearance recess is formed over the entire periphery of the flange portion 5.

保持器４は円環状に形成されており、この保持器４の周面部には、円錐ころ３を収容保持する複数の保持器ポケット４ａが形成されている。また、保持器４は円錐ころ３が内輪１の小径側に移動するのを抑制するための爪部８を大径側端部に有しており、この爪部８の先端部は逃げ溝７内に挿入されている。この爪部８は、大径側を傾斜させた楔形とすることにより大径方向には前記逃げ溝７へ挿入しやすく、前記爪部８が前記逃げ溝７から小径方向には脱落し難い形状となっている。なお、この爪部８は円環状でなくても良く、少なくとも一ヶ所あれば良い。
保持器４の保持器ポケット４ａは円錐ころ３の外形形状に相似した円錐面形状に形成されており、保持器４と円錐ころ３を一体に組立てられるようにしている。 The cage 4 is formed in an annular shape, and a plurality of cage pockets 4 a for accommodating and holding the tapered rollers 3 are formed on the peripheral surface portion of the cage 4. Further, the retainer 4 has a claw portion 8 for suppressing the tapered roller 3 from moving to the small diameter side of the inner ring 1 at the large diameter side end portion, and the tip end portion of the claw portion 8 is a relief groove 7. Has been inserted inside. The claw portion 8 is formed in a wedge shape with the large diameter side inclined so that the claw portion 8 can be easily inserted into the escape groove 7 in the large diameter direction and the claw portion 8 is difficult to drop out from the escape groove 7 in the small diameter direction. It has become. In addition, this nail | claw part 8 does not need to be an annular shape, and should just be at least one place.
The cage pocket 4a of the cage 4 is formed in a conical surface shape similar to the outer shape of the tapered roller 3, so that the cage 4 and the tapered roller 3 can be assembled together.

爪部８は、図２に示すように、逃げ溝７の内側の壁面部７ａと対向する内側面８ａを有している。また、爪部８は逃げ溝７の外側の壁面部７ｂと対向する外側面８ｂを有している。すなわち、逃げ溝７内に挿入された爪部８は、その内側面８ａ、外側面８ｂ、及び先端部が逃げ溝７の内側の壁面部７ａ、外側の壁面部７ｂ、及び底面部７ｃから所定の間隔を有している。内輪１の軌道面１ａが円錐ころ３の転動面（周面部）に接触すると共に鍔部５が円錐ころ３の大径側端面３ａ（図１参照）に接触し、かつ保持器４の中心軸が内輪１の中心軸と一致するとき、爪部８の内側面８ａと逃げ溝７の内側の壁面部７ａとの間の軸方向隙間をａ、円錐ころ３の大径側端面３ａと保持器４の保持器ポケット４ａとの間の軸方向隙間をｂ（図３参照）、爪部８の外側面８ｂと逃げ溝７の外側の壁面部７ｂとの間の軸方向隙間をｃ、円錐ころ３の小径側端面３ｂと保持器４の保持器ポケット４ａとの間の軸方向隙間をｄ（図３参照）とすると、円錐ころ３と保持器４の保持器ポケット４ａとの間の軸方向隙間ｂ，ｄはａ＞ｂ，ｃ＞ｄとなっている。   As shown in FIG. 2, the claw portion 8 has an inner surface 8 a that faces the inner wall surface portion 7 a of the escape groove 7. Further, the claw portion 8 has an outer surface 8 b that faces the outer wall surface portion 7 b of the escape groove 7. That is, the claw portion 8 inserted into the escape groove 7 has an inner side surface 8a, an outer side surface 8b, and a tip portion predetermined from the inner wall surface portion 7a, the outer wall surface portion 7b, and the bottom surface portion 7c. Have an interval of The raceway surface 1a of the inner ring 1 is in contact with the rolling surface (circumferential surface portion) of the tapered roller 3, the flange portion 5 is in contact with the large-diameter side end surface 3a (see FIG. 1) of the tapered roller 3, and the center of the cage 4 When the shaft coincides with the central axis of the inner ring 1, the axial clearance between the inner side surface 8 a of the claw portion 8 and the inner wall surface portion 7 a of the clearance groove 7 is retained with a, and the large-diameter side end surface 3 a of the tapered roller 3 is retained. The axial gap between the cage 4 and the cage pocket 4a is b (see FIG. 3), the axial gap between the outer surface 8b of the claw 8 and the outer wall surface 7b of the escape groove 7 is c, and the cone A shaft between the tapered roller 3 and the cage pocket 4a of the cage 4 is d (refer to FIG. 3), where d is an axial clearance between the small diameter side end surface 3b of the roller 3 and the cage pocket 4a of the cage 4. The direction gaps b and d are a> b and c> d.

このような構成において、一体となった内輪１、円錐ころ３および保持器４が外輪２と組合わされない状態では、保持器４が内輪１の小径側に移動すると、保持器４の大径側端部に設けられた爪部８の内側面８ａが内輪１の大径側端部に設けられた逃げ溝７の内側の壁面部７ａに当接する。これにより、内輪１の小径側端部に鍔部がなくても保持器４が内輪１の小径側から抜け出ることを防止でき、図１９に示した従来例のように、内輪１の小径側端部に鍔部６を設けたり、保持器４の小径側端部を加締めたりする必要がないので、コストの低減を図ることができる。   In such a configuration, when the integrated inner ring 1, tapered roller 3 and cage 4 are not combined with the outer ring 2, when the cage 4 moves to the small diameter side of the inner ring 1, the large diameter side of the cage 4 An inner side surface 8 a of the claw portion 8 provided at the end portion contacts an inner wall surface portion 7 a of the escape groove 7 provided at the large-diameter side end portion of the inner ring 1. Accordingly, the cage 4 can be prevented from coming out from the small diameter side of the inner ring 1 even if there is no flange at the small diameter side end of the inner ring 1, and the small diameter side end of the inner ring 1 can be prevented as in the conventional example shown in FIG. Since it is not necessary to provide the flange portion 6 in the portion or crimp the small diameter side end portion of the cage 4, the cost can be reduced.

また、内輪１、円錐ころ３および保持器４が外輪２と組合わされ、円錐ころ軸受として運転されるときには、保持器４が内輪１の小径側に移動すると、爪部８の内側面８ａが逃げ溝７の内側の壁面部７ａに接触する前に保持器４の保持器ポケット４ａが円錐ころ３の大径側端面３ａに当接する。このとき、ころ３は外輪２があるので、軸方向に移動できない。逆に、保持器４が内輪１の大径側に移動すると、爪部８の外側面８ｂが逃げ溝７の外側の壁面部７ｂに接触する前に保持器４の保持器ポケット４ａが円錐ころ３の小径側端面３ｂに当接する。これにより、保持器４が軸方向に移動しても爪部８が鍔部５と接触することがないので、内輪１や爪部８に摩耗が生じたり、爪部８が鍔部５に接触することによって潤滑剤の流れが阻害されたりすることを抑制することができる。   Further, when the inner ring 1, the tapered roller 3 and the cage 4 are combined with the outer ring 2 and operated as a tapered roller bearing, when the cage 4 moves to the smaller diameter side of the inner ring 1, the inner side surface 8 a of the claw portion 8 escapes. The cage pocket 4 a of the cage 4 abuts on the large-diameter side end surface 3 a of the tapered roller 3 before coming into contact with the wall surface portion 7 a inside the groove 7. At this time, since the roller 3 has the outer ring 2, it cannot move in the axial direction. Conversely, when the cage 4 moves to the larger diameter side of the inner ring 1, the cage pocket 4 a of the cage 4 is tapered before the outer surface 8 b of the claw 8 contacts the wall surface 7 b outside the escape groove 7. 3 abuts on the small diameter side end face 3b. As a result, even if the cage 4 moves in the axial direction, the claw portion 8 does not come into contact with the flange portion 5, so that the inner ring 1 and the claw portion 8 are worn or the claw portion 8 contacts the flange portion 5. By doing so, it is possible to prevent the flow of the lubricant from being hindered.

なお、上述した第１の実施形態では、円錐ころ３を保持する保持器４としてプレス成形保持器を示したが、図４に示す第２の実施形態のように、樹脂製保持器を用いてもよい。また、上述した第１の実施形態では、内輪１の軌道面１ａが円錐ころ３の転動面（周面部）に接触すると共に鍔部５が円錐ころ３の端面に接触し、かつ保持器４の中心軸が内輪１の中心軸と一致するとき、円錐ころ３と保持器４の保持器ポケット４ａとの軸方向隙間ｂ，ｄを逃げ溝７と爪部８との軸方向隙間ａ，ｃより小さくしたが、円錐ころ３と保持器４の保持器ポケット４ａとの軸方向隙間を小さくする代わりに、図４〜図６に示す第２の実施形態のように、円錐ころ３の動きを規制する突起部９，１０を保持器ポケット４ａの両端に設け、円錐ころ３と突起部９，１０との軸方向隙間ｂ，ｄを爪部８と逃げ溝７との軸方向隙間ａ，ｃに対してａ＞ｂ，ｃ＞ｄとしてもよい。この場合、保持器円環部の中心径が円錐ころ３のＰＣＤより大きい場合は、突起部９，１０を円錐ころ３の中心に近い箇所に設けることにより、周速が小さくなるので、保持器４と円錐ころ３の軸方向の接触による摩耗量を小さく抑えることができる。   In the first embodiment described above, a press-molded cage is shown as the cage 4 that holds the tapered rollers 3, but a resin cage is used as in the second embodiment shown in FIG. Also good. Further, in the first embodiment described above, the raceway surface 1 a of the inner ring 1 contacts the rolling surface (circumferential surface portion) of the tapered roller 3, the flange portion 5 contacts the end surface of the tapered roller 3, and the cage 4. When the central axis of the inner ring 1 coincides with the central axis of the inner ring 1, the axial gaps b, d between the tapered roller 3 and the cage pocket 4 a of the cage 4 are passed through the axial gaps a, c between the escape groove 7 and the claw portion 8. Although smaller, instead of reducing the axial clearance between the tapered roller 3 and the cage pocket 4a of the cage 4, the movement of the tapered roller 3 is made as in the second embodiment shown in FIGS. Protruding portions 9 and 10 to be controlled are provided at both ends of the cage pocket 4a, and axial gaps b and d between the tapered roller 3 and the protruding portions 9 and 10 are provided as axial gaps a and c between the claw portion 8 and the escape groove 7. Alternatively, a> b and c> d may be satisfied. In this case, when the center diameter of the retainer ring portion is larger than the PCD of the tapered roller 3, the peripheral speed is reduced by providing the projections 9 and 10 near the center of the tapered roller 3. The amount of wear due to axial contact between 4 and the tapered roller 3 can be kept small.

さらに、ａ＞ｂ、ｃ＞ｄとすることにより、保持器４の爪部８が逃げ溝７の側面に当たる前に保持器４の突起部９，１０が円錐ころ３の端面と接触する。このため、保持器４の爪部８と逃げ溝７の側面が接触するときのすべり速度よりも、保持器４の突起部９，１０が円錐ころ３の端面と接触するときのすべり速度の方が小さいので、摩擦力が小さく、摩耗量を小さく抑えることができる。   Further, by setting a> b and c> d, the protrusions 9 and 10 of the cage 4 come into contact with the end surface of the tapered roller 3 before the claw portion 8 of the cage 4 hits the side surface of the escape groove 7. Therefore, the sliding speed when the protrusions 9 and 10 of the cage 4 are in contact with the end surface of the tapered roller 3 is higher than the sliding speed when the claw portion 8 of the cage 4 and the side surface of the escape groove 7 are in contact. Is small, the frictional force is small and the wear amount can be kept small.

第１及び第２の実施形態では、保持器４の大径側端部に設けた爪部８を内輪１に設けた逃げ溝７の両端面から所定の間隔を有するように挿入させたが、図７に示す第３の実施形態のように、爪部８を内輪１の端面（大径側端面）１ｂから離間するように設置してもよい。この場合、内輪１の軌道面１ａが円錐ころ３の転動面（周面部）に接触すると共に鍔部５が円錐ころ３の端面に接触し、かつ保持器４の中心軸が内輪１の中心軸と一致するとき、内輪１の端面１ｂと鍔部８との間の案内隙間ａを円錐ころ３の端面と保持器４の保持器ポケット４ａとの間の隙間ｂより大きくすることにより（ａ＞ｂ）、爪部８と内輪端面１ｂとの接触による摩耗を防止することができる。   In the first and second embodiments, the claw portion 8 provided at the large-diameter side end of the cage 4 is inserted so as to have a predetermined interval from both end surfaces of the escape groove 7 provided in the inner ring 1. As in the third embodiment shown in FIG. 7, the claw portion 8 may be installed so as to be separated from the end surface (large diameter side end surface) 1 b of the inner ring 1. In this case, the raceway surface 1 a of the inner ring 1 contacts the rolling surface (circumferential surface portion) of the tapered roller 3, the flange portion 5 contacts the end surface of the tapered roller 3, and the central axis of the cage 4 is the center of the inner ring 1. When the axis coincides with the shaft, the guide gap a between the end face 1b of the inner ring 1 and the flange 8 is made larger than the gap b between the end face of the tapered roller 3 and the cage pocket 4a of the cage 4 (a > B) Wear due to contact between the claw portion 8 and the inner ring end face 1b can be prevented.

また、第３の実施形態では、第１及び第２の実施形態のように、保持器４の爪部８を挿入する逃げ溝を内輪１に設ける必要はないが、保持器４が内輪１の端面１ｂから突出するため、軸方向寸法は第１及び第２の実施形態の方が小さく設定できる。
図８（ａ）〜（ｃ）は、本発明の第４の実施形態として、爪部８の好ましい形状を示す図である。例えば、図８（ａ）に示すように、爪部８は、逃げ溝７に対向する端部において、大径側に丸みが形成されてもよい。また、図８（ｂ）に示すように、爪部８は、逃げ溝７に対向する端部において、大径側に切り落とした形状としてもよい。更に、図８（ｃ）に示すように、爪部８は、大径側を傾斜させた楔形をなすと共に、小径側に湾曲した切欠きが形成されてもよい。 Further, in the third embodiment, unlike the first and second embodiments, it is not necessary to provide the inner ring 1 with a clearance groove for inserting the claw portion 8 of the retainer 4, but the retainer 4 is provided on the inner ring 1. Since it protrudes from the end surface 1b, the axial dimension can be set smaller in the first and second embodiments.
FIGS. 8A to 8C are views showing a preferable shape of the claw portion 8 as the fourth embodiment of the present invention. For example, as shown in FIG. 8A, the claw portion 8 may be rounded on the large diameter side at the end facing the escape groove 7. Further, as shown in FIG. 8B, the claw portion 8 may have a shape cut off to the large diameter side at the end portion facing the escape groove 7. Further, as shown in FIG. 8C, the claw portion 8 may have a wedge shape in which the large diameter side is inclined, and a notch that is curved toward the small diameter side may be formed.

図９は、本発明の第５の実施形態を示す図である。図９に示すように、第５の実施形態では、逃げ溝７が外輪２の小径側端部に設けられている。また、爪部８は、逃げ溝７の両端面に対して所定の間隔を有して逃げ溝７に挿入されるように、保持器４の小径側端部に設けられている。また、円錐ころ３の動きを規制する突起部９，１０が保持器ポケット４ａの両端に設けられている。更に、内輪１の軌道面１ａが円錐ころ３の転動面（周面部）に接触すると共に鍔部５が円錐ころ３の端面３ａに接触し、かつ保持器４の中心軸が内輪１の中心軸と一致するとき、爪部８の内側面８ａと逃げ溝７の内側の壁面部７ａとの間の軸方向隙間をａ、円錐ころ３の小径側端面３ｂと突起部１０との間の軸方向隙間をｂ、爪部８の外側面８ｂと逃げ溝７の外側の壁面部７ｂとの間の軸方向隙間をｃ、円錐ころ３の大径側端面３ａと突起部９との間の軸方向隙間をｄとすると、円錐ころ３と保持器４の保持器ポケット４ａとの間の軸方向隙間ｂ，ｄはａ＞ｂ，ｃ＞ｄとなっている。   FIG. 9 is a diagram showing a fifth embodiment of the present invention. As shown in FIG. 9, in the fifth embodiment, the escape groove 7 is provided at the small diameter side end of the outer ring 2. Further, the claw portion 8 is provided at the end portion on the small diameter side of the retainer 4 so as to be inserted into the escape groove 7 with a predetermined interval with respect to both end faces of the escape groove 7. Protrusions 9 and 10 that restrict the movement of the tapered roller 3 are provided at both ends of the cage pocket 4a. Further, the raceway surface 1 a of the inner ring 1 contacts the rolling surface (circumferential surface portion) of the tapered roller 3, the flange portion 5 contacts the end surface 3 a of the tapered roller 3, and the central axis of the cage 4 is the center of the inner ring 1. When it coincides with the axis, the axial clearance between the inner surface 8a of the claw 8 and the inner wall surface 7a of the escape groove 7 is a, and the axis between the small diameter side end surface 3b of the tapered roller 3 and the projection 10 B is the axial clearance between the outer surface 8 b of the claw 8 and the outer wall surface 7 b of the relief groove 7, and the axis is between the large-diameter end surface 3 a of the tapered roller 3 and the projection 9. When the directional gap is d, the axial gaps b and d between the tapered roller 3 and the cage pocket 4a of the cage 4 are a> b and c> d.

このように、逃げ溝７及び爪部８の設置位置を外輪２側に規定することにより、外輪２と保持器４との組み立てを容易にし、外輪２からの保持器４の脱落を防止することができる。
図１０は、本発明の第６の実施形態を示す図である。図１０に示すように、第６の実施形態では、内輪１の軌道面１ａに対して所定の間隙を形成する突起部１１が、保持器４の小径側端部に形成されている。 Thus, by defining the installation positions of the escape groove 7 and the claw portion 8 on the outer ring 2 side, the assembly of the outer ring 2 and the retainer 4 is facilitated, and the retainer 4 is prevented from falling off from the outer ring 2. Can do.
FIG. 10 is a diagram showing a sixth embodiment of the present invention. As shown in FIG. 10, in the sixth embodiment, a protrusion 11 that forms a predetermined gap with respect to the raceway surface 1 a of the inner ring 1 is formed at the small diameter side end of the cage 4.

このように、小径側において、内輪１と保持器４との間から軸受内に流入する油を突起部１１が抑制することによって、軸受の低トルク化を実現することができる。
図１１は、本発明の第７の実施形態を示す図である。図１１に示すように、第７の実施形態では、内輪１の軌道面１ａに対して所定の間隙を形成する突起部１１が、保持器４の小径側端部に形成され、突起部１１が内輪１の小径側端部の一部を覆うように形成されている。 Thus, on the small diameter side, the protrusion 11 suppresses the oil flowing into the bearing from between the inner ring 1 and the cage 4, thereby realizing a reduction in torque of the bearing.
FIG. 11 is a diagram showing a seventh embodiment of the present invention. As shown in FIG. 11, in the seventh embodiment, a protrusion 11 that forms a predetermined gap with respect to the raceway surface 1 a of the inner ring 1 is formed at the end on the small diameter side of the cage 4, and the protrusion 11 is The inner ring 1 is formed so as to cover a part of the end portion on the small diameter side.

このように、軸方向にも保持器４と内輪１とを接近させることによって、軸受内への油の流入を更に抑制することができる。なお、保持器４は、保持器ポケット４ａ内に収容される円錐ころ３により軸方向に案内されているため、内輪１と保持器４とが軸方向で接触することはない。従って、保持器４の回転における抵抗を低減し、軸受の低トルク化を更に向上させることができる。   Thus, the inflow of oil into the bearing can be further suppressed by bringing the cage 4 and the inner ring 1 closer in the axial direction. Since the cage 4 is guided in the axial direction by the tapered rollers 3 accommodated in the cage pocket 4a, the inner ring 1 and the cage 4 do not contact in the axial direction. Accordingly, the resistance in rotation of the cage 4 can be reduced and the torque reduction of the bearing can be further improved.

図１２は、本発明の第８の実施形態を示す図である。図１２に示すように、第８の実施形態では、内輪１の軌道面１ａに対して所定の間隙を形成する突起部１１が、保持器４の小径側端部に形成され、内輪１の大径側端面１ｂから離間するように爪部８が保持器４の大径側端部に形成されている。
このように、爪部８を形成することにより、内輪１と、保持器４と、円錐ころ３とを一体化でき、組み立てを容易にすることができる。 FIG. 12 is a diagram showing an eighth embodiment of the present invention. As shown in FIG. 12, in the eighth embodiment, a protrusion 11 that forms a predetermined gap with respect to the raceway surface 1 a of the inner ring 1 is formed at the small-diameter side end of the retainer 4, and the inner ring 1 is large. A claw portion 8 is formed at the large-diameter side end portion of the cage 4 so as to be separated from the radial-side end surface 1b.
Thus, by forming the claw portion 8, the inner ring 1, the cage 4, and the tapered roller 3 can be integrated, and assembly can be facilitated.

図１３は、本発明の第９の実施形態を示す図である。図１３に示すように、第９の実施形態では、内輪１と、内輪１の外周面に形成された軌道面１ａと対向する軌道面２ａを有する外輪２と、内輪１の軌道面１ａと外輪２の軌道面２ａとの間に複数の円錐ころ３が設けられている。円錐ころ３は、保持器４に設けられた複数の保持器ポケット４ａに収容保持される。保持器４の小径側端部には、内輪１の軌道面１ａに対して所定の間隙を形成する突起部１１が形成されている。突起部１１の小径側の傾斜面１１ａは、回転軸に直交する方向に対して所定の角度で傾斜している。   FIG. 13 is a diagram showing a ninth embodiment of the present invention. As shown in FIG. 13, in the ninth embodiment, an inner ring 1, an outer ring 2 having a raceway surface 2 a facing the raceway surface 1 a formed on the outer peripheral surface of the inner ring 1, a raceway surface 1 a of the inner ring 1, and an outer ring A plurality of tapered rollers 3 are provided between the two raceway surfaces 2a. The tapered roller 3 is accommodated and held in a plurality of cage pockets 4 a provided in the cage 4. A protrusion 11 that forms a predetermined gap with respect to the raceway surface 1 a of the inner ring 1 is formed at the end on the small diameter side of the cage 4. The inclined surface 11a on the small diameter side of the protrusion 11 is inclined at a predetermined angle with respect to the direction orthogonal to the rotation axis.

このように、回転軸に直交する方向に対して所定の角度で傾斜させた傾斜面１１ａを突起部１１の小径側に形成することにより、内輪及び外輪が相対的に回転した際に、遠心力によって保持器４に付着している油が半径方向外側に吹き飛ばされる。従って、円錐ころ軸受が本来有しているポンプ作用により、円錐ころの小径側から大径側への油の流れに抗って軸受内部への油の流入を低減するので、軸受の低トルク化を実現することができる。   In this way, by forming the inclined surface 11a inclined at a predetermined angle with respect to the direction orthogonal to the rotation axis on the small diameter side of the protrusion 11, when the inner ring and the outer ring rotate relatively, the centrifugal force As a result, the oil adhering to the cage 4 is blown off radially outward. Therefore, the pumping action inherent to the tapered roller bearing reduces the inflow of oil into the bearing against the oil flow from the small diameter side to the large diameter side of the tapered roller. Can be realized.

図１４は、本発明の第１０の実施形態を示す図である。図１４に示すように、第１０の実施形態では、内輪１と、内輪１の外周面に形成された軌道面１ａと対向する軌道面２ａを有する外輪２と、内輪１の軌道面１ａと外輪２の軌道面２ａとの間に複数の円錐ころ３が設けられている。円錐ころ３は、保持器４に設けられた複数の保持器ポケット４ａに収容保持される。保持器４の小径側端部には、内輪１の軌道面１ａに対して所定の間隙を形成する突起部１１が形成されている。突起部１１の小径側の傾斜面１１ａは、回転軸に直交する方向に対して所定の角度で傾斜している。更に、内輪１の大径側端部に形成された鍔部５には、逃げ溝７が形成されている。保持器４の大径側端部には、逃げ溝７に挿入される爪部８が形成されている。そして、円錐ころ３と保持器４の保持器ポケット４ａとの間の軸方向隙間は、爪部８が鍔部５と接触しないように規定されている。   FIG. 14 is a diagram showing a tenth embodiment of the present invention. As shown in FIG. 14, in the tenth embodiment, the inner ring 1, the outer ring 2 having the raceway surface 2 a facing the raceway surface 1 a formed on the outer peripheral surface of the inner ring 1, the raceway surface 1 a of the inner ring 1, and the outer ring A plurality of tapered rollers 3 are provided between the two raceway surfaces 2a. The tapered roller 3 is accommodated and held in a plurality of cage pockets 4 a provided in the cage 4. A protrusion 11 that forms a predetermined gap with respect to the raceway surface 1 a of the inner ring 1 is formed at the end on the small diameter side of the cage 4. The inclined surface 11a on the small diameter side of the protrusion 11 is inclined at a predetermined angle with respect to the direction orthogonal to the rotation axis. Further, a clearance groove 7 is formed in the flange portion 5 formed at the large diameter side end portion of the inner ring 1. A claw portion 8 to be inserted into the escape groove 7 is formed at the end portion on the large diameter side of the cage 4. The axial gap between the tapered roller 3 and the cage pocket 4 a of the cage 4 is defined so that the claw portion 8 does not contact the flange portion 5.

図１５は、本発明の第１１の実施形態を示す図である。図１６は、図１５のＣ部を拡大して示す図である。図１５及び図１６に示すように、第１１の実施形態では、大径側端部に鍔部５が形成された内輪１の小径側端部に逃げ溝７が設けられている。また、爪部８は、逃げ溝７の両端面に所定の間隔を有して逃げ溝７に挿入されるように、保持器４の小径側端部に設けられている。更に、内輪１の軌道面１ａが円錐ころ３の転動面（周面部）に接触すると共に鍔部５が円錐ころ３の端面３ａに接触し、かつ保持器４の中心軸が内輪１の中心軸と一致するとき、爪部８の内側面８ａと逃げ溝７の内側の壁面部７ａとの間の軸方向隙間をａ、円錐ころ３の小径側端面３ｂと保持器４の保持器ポケット４ａとの間の軸方向隙間をｂ、爪部８の外側面８ｂと逃げ溝７の外側の壁面部７ｂとの間の軸方向隙間をｃ、円錐ころ３の大径側端面３ａと保持器４の保持器ポケット４ａとの間の軸方向隙間をｄとすると、円錐ころ３と保持器４の保持器ポケット４ａとの間の軸方向隙間ｂ，ｄはａ＞ｂ，ｃ＞ｄとなっている。   FIG. 15 is a diagram showing an eleventh embodiment of the present invention. FIG. 16 is an enlarged view of a portion C in FIG. As shown in FIGS. 15 and 16, in the eleventh embodiment, the escape groove 7 is provided at the small diameter side end portion of the inner ring 1 in which the flange portion 5 is formed at the large diameter side end portion. Further, the claw portion 8 is provided at the end portion on the small diameter side of the cage 4 so as to be inserted into the escape groove 7 with a predetermined interval between both end faces of the escape groove 7. Further, the raceway surface 1 a of the inner ring 1 contacts the rolling surface (circumferential surface portion) of the tapered roller 3, the flange portion 5 contacts the end surface 3 a of the tapered roller 3, and the central axis of the cage 4 is the center of the inner ring 1. When it coincides with the shaft, the axial clearance between the inner surface 8a of the claw 8 and the inner wall surface 7a of the escape groove 7 is a, the small diameter side end surface 3b of the tapered roller 3 and the cage pocket 4a of the cage 4. B, the axial clearance between the outer surface 8b of the claw portion 8 and the outer wall surface portion 7b of the relief groove 7, c, the large-diameter end surface 3a of the tapered roller 3 and the cage 4. When the axial gap between the cage pocket 4a and the cage pocket 4a is d, the axial gaps b and d between the tapered roller 3 and the cage pocket 4a of the cage 4 are a> b, c> d. Yes.

このように、大径側端部に鍔部５が形成された内輪１の小径側端部に逃げ溝７を形成し、該逃げ溝７に挿入される爪部８を保持器４に設けることにより、油の流入を制限し、攪拌抵抗を軽減し、軸受の低トルク化を実現する。このとき、上記ａ＞ｂ，ｃ＞ｄの関係を満たすと、保持器４の爪部８が逃げ溝７の側面に当たる前に保持器４の保持器ポケット４ａ，４ａが円錐ころ３の端面と接触する。このため、保持器４の爪部８と逃げ溝７の側面が接触するときのすべり速度よりも、保持器４の保持器ポケット４ａ，４ａが円錐ころ３の端面と接触するときのすべり速度の方が小さいので、摩擦力が小さく、摩耗量を小さく抑えることができる。   Thus, the escape groove 7 is formed in the small diameter side end portion of the inner ring 1 in which the flange portion 5 is formed at the large diameter side end portion, and the claw portion 8 inserted into the escape groove 7 is provided in the cage 4. Therefore, the inflow of oil is limited, the stirring resistance is reduced, and the torque of the bearing is reduced. At this time, if the relations a> b and c> d are satisfied, the cage pockets 4a and 4a of the cage 4 are connected to the end surface of the tapered roller 3 before the claw portion 8 of the cage 4 hits the side surface of the escape groove 7. Contact. For this reason, the sliding speed when the cage pockets 4a and 4a of the cage 4 are in contact with the end surface of the tapered roller 3 is higher than the sliding speed when the claw portion 8 of the cage 4 and the side surface of the escape groove 7 are in contact. Therefore, the frictional force is small and the wear amount can be kept small.

また、爪部８の断面形状は、図１６（ａ）に示すように、逃げ溝７に対向する端部において、大径側に切り落とした形状としてもよい。また、図１６（ｂ）に示すように、爪部８の断面形状に、大径側を傾斜させた楔形をなすと共に、小径側に湾曲した切欠きが形成されてもよい。更に、図１６（ｃ）に示すように、爪部８の断面形状は、逃げ溝７に対向する端部において、大径側に丸みが形成されてもよい。   Moreover, the cross-sectional shape of the nail | claw part 8 is good also as a shape cut off to the large diameter side in the edge part which opposes the escape groove 7, as shown to Fig.16 (a). In addition, as shown in FIG. 16B, the cross-sectional shape of the claw portion 8 may be formed in a wedge shape in which the large diameter side is inclined and a notch that is curved on the small diameter side. Furthermore, as shown in FIG. 16C, the claw portion 8 may have a cross-sectional shape that is rounded on the large diameter side at the end facing the escape groove 7.

このように、爪部８の断面形状を、内輪１の大径方向には入りやすく、内輪１の小径方向からは外れにくい構造となり、組み立てを容易にすることができる。特に、本実施形態では、内輪１の小径側に鍔部を形成せず、内輪１の小径側に逃げ溝７を形成し、該逃げ溝７に爪部８を挿入することで、内輪１と保持器４とを組み立て、逃げ溝７と爪部８とによって間隙を形成している。これにより、内輪１の小径側に鍔部を形成する工程と、保持器４の小径側を加締める工程とを省略することができるので、製造コストを低減することができる。具体的には、内輪１に逃げ溝７を形成するコストは、従来のように、鍔部及び円筒部を形成するコストに比べて低いので、製造コストを低減することができる。   In this way, the cross-sectional shape of the claw portion 8 is easy to enter in the large-diameter direction of the inner ring 1 and is difficult to come off from the small-diameter direction of the inner ring 1, thereby facilitating assembly. In particular, in this embodiment, the inner ring 1 is not formed on the small diameter side of the inner ring 1, the clearance groove 7 is formed on the small diameter side of the inner ring 1, and the claw part 8 is inserted into the clearance groove 7, thereby The cage 4 is assembled, and the clearance groove 7 and the claw portion 8 form a gap. Thereby, since the process of forming a collar part on the small diameter side of the inner ring 1 and the process of caulking the small diameter side of the cage 4 can be omitted, the manufacturing cost can be reduced. Specifically, since the cost of forming the relief groove 7 in the inner ring 1 is lower than the cost of forming the flange portion and the cylindrical portion as in the prior art, the manufacturing cost can be reduced.

図１７は、本発明の第１２の実施形態を示す図である。図１７に示すように、第１２の実施形態では、保持器４の小径側端面に突起１１を設け、突起部１１の小径側の面１１ａは、回転軸に直交する方向に対して所定の角度で傾斜させている。
このように、保持器４の小径側端面に突起１１を設け、突起部１１を所定の角度で傾斜させることで、内輪１及び外輪２が相対的に回転した際に、突起１１よりも外周側に付着している油が半径方向外側に吹き飛ばされる。従って、円錐ころ軸受が本来有しているポンプ作用により、円錐ころの小径側から大径側への油の流れに抗って軸受内部への油の流入を低減するので、軸受の低トルク化を実現できる。 FIG. 17 is a diagram showing a twelfth embodiment of the present invention. As shown in FIG. 17, in the twelfth embodiment, a protrusion 11 is provided on the end surface on the small diameter side of the cage 4, and the surface 11a on the small diameter side of the protrusion 11 has a predetermined angle with respect to the direction orthogonal to the rotation axis. It is inclined at.
As described above, the protrusion 11 is provided on the end surface on the small diameter side of the cage 4, and the protrusion 11 is inclined at a predetermined angle, so that the inner ring 1 and the outer ring 2 are relatively rotated more than the protrusion 11 when the inner ring 1 and the outer ring 2 are relatively rotated. The oil adhering to is blown off radially outward. Therefore, the pumping action inherent to the tapered roller bearing reduces the inflow of oil into the bearing against the oil flow from the small diameter side to the large diameter side of the tapered roller. Can be realized.

図１８は、本発明の第１３の実施形態を示す図である。図１８に示すように、第１３の実施形態では、逃げ溝７が外輪２の大径側端部に設けられている。また、爪部８は、逃げ溝７の両端面に対して所定の間隔を有して逃げ溝７に挿入されるように、保持器４の大径側端部に設けられている。また、円錐ころ３の動きを規制する突起部９，１０が保持器ポケット４ａの両端に設けられている。更に、内輪１の軌道面１ａが円錐ころ３の転動面（周面部）に接触すると共に鍔部５が円錐ころ３の端面３ａに接触し、かつ保持器４の中心軸が内輪１の中心軸と一致するとき、爪部８の内側面８ａと逃げ溝７の内側の壁面部７ａとの間の軸方向隙間をａ、円錐ころ３の大径側端面３ａと突起部１０との間の軸方向隙間をｂ、爪部８の外側面８ｂと逃げ溝７の外側の壁面部７ｂとの間の軸方向隙間をｃ、円錐ころ３の小径側端面３ｂと突起部９との間の軸方向隙間をｄとすると、円錐ころ３と保持器４の保持器ポケット４ａとの間の軸方向隙間ｂ，ｄはａ＞ｂ，ｃ＞ｄとなっている。   FIG. 18 is a diagram showing a thirteenth embodiment of the present invention. As shown in FIG. 18, in the thirteenth embodiment, the escape groove 7 is provided at the large-diameter side end of the outer ring 2. Further, the claw portion 8 is provided at the end portion on the large diameter side of the retainer 4 so as to be inserted into the escape groove 7 with a predetermined interval with respect to both end faces of the escape groove 7. Protrusions 9 and 10 that restrict the movement of the tapered roller 3 are provided at both ends of the cage pocket 4a. Further, the raceway surface 1 a of the inner ring 1 contacts the rolling surface (circumferential surface portion) of the tapered roller 3, the flange portion 5 contacts the end surface 3 a of the tapered roller 3, and the central axis of the cage 4 is the center of the inner ring 1. When it coincides with the axis, the axial clearance between the inner surface 8a of the claw 8 and the inner wall surface 7a of the clearance groove 7 is a, and between the large-diameter side end surface 3a of the tapered roller 3 and the projection 10 The axial gap is b, the axial gap between the outer surface 8b of the claw 8 and the outer wall surface 7b of the relief groove 7 is c, and the axis between the small diameter side end surface 3b of the tapered roller 3 and the projection 9 When the directional gap is d, the axial gaps b and d between the tapered roller 3 and the cage pocket 4a of the cage 4 are a> b and c> d.

このように、逃げ溝７及び爪部８の設置位置を外輪２側に規定することにより、外輪２と保持器４との組み立てを容易にし、外輪２からの保持器４の脱落を防止することができる。
以上説明したように、本発明によれば、回転軸に直交する方向に対して所定の角度で傾斜させた傾斜面１１ａを突起部１１の小径側に形成することにより、円錐ころの小径側から大径側への油の流れに抗って軸受内部への油の流入を低減するので、軸受の低トルク化を実現することができる。また、逃げ溝７の両端面に対して所定の間隔を有して位置する爪部８を保持器４に設けたので、内輪１と、保持器４と、円錐ころ３とを一体化することができ、結果として、軸受の組み立てを容易にすることができる。 Thus, by defining the installation positions of the escape groove 7 and the claw portion 8 on the outer ring 2 side, the assembly of the outer ring 2 and the retainer 4 is facilitated, and the retainer 4 is prevented from falling off from the outer ring 2. Can do.
As described above, according to the present invention, the inclined surface 11a that is inclined at a predetermined angle with respect to the direction orthogonal to the rotation axis is formed on the small diameter side of the projection 11 so that the small diameter side of the tapered roller can be removed. Since the inflow of oil into the bearing is reduced against the flow of oil to the large diameter side, the torque of the bearing can be reduced. Further, since the retainer 4 is provided with the claw portion 8 positioned at a predetermined interval with respect to both end faces of the relief groove 7, the inner ring 1, the retainer 4, and the tapered roller 3 are integrated. As a result, the assembly of the bearing can be facilitated.

本発明の第１の実施形態に係る円錐ころ軸受の断面図である。It is sectional drawing of the tapered roller bearing which concerns on the 1st Embodiment of this invention. 図１のＡ部を拡大して示す図である。It is a figure which expands and shows the A section of FIG. 図１に示す円錐ころ軸受の円錐ころと保持器との間の軸方向隙間を示す図である。It is a figure which shows the axial direction clearance gap between the tapered roller of the tapered roller bearing shown in FIG. 1, and a holder | retainer. 本発明の第２の実施形態に係る円錐ころ軸受の断面図である。It is sectional drawing of the tapered roller bearing which concerns on the 2nd Embodiment of this invention. 図４のＢ部を拡大して示す図である。It is a figure which expands and shows the B section of FIG. 図４に示す円錐ころ軸受の円錐ころと保持器に設けられた突起部との間の軸方向隙間を示す図である。It is a figure which shows the axial direction clearance gap between the tapered roller of the tapered roller bearing shown in FIG. 4, and the projection part provided in the holder | retainer. 本発明の第３の実施形態を示す図である。It is a figure which shows the 3rd Embodiment of this invention. 本発明の第４の実施形態を示す図である。It is a figure which shows the 4th Embodiment of this invention. 本発明の第５の実施形態を示す図である。It is a figure which shows the 5th Embodiment of this invention. 本発明の第６の実施形態を示す図である。It is a figure which shows the 6th Embodiment of this invention. 本発明の第７の実施形態を示す図である。It is a figure which shows the 7th Embodiment of this invention. 本発明の第８の実施形態を示す図である。It is a figure which shows the 8th Embodiment of this invention. 本発明の第９の実施形態を示す図である。It is a figure which shows the 9th Embodiment of this invention. 本発明の第１０の実施形態を示す図である。It is a figure which shows the 10th Embodiment of this invention. 本発明の第１１の実施形態を示す図である。It is a figure which shows the 11th Embodiment of this invention. 図１５のＣ部を拡大して示す図である。It is a figure which expands and shows the C section of FIG. 本発明の第１２の実施形態を示す図である。It is a figure which shows the 12th Embodiment of this invention. 本発明の第１３の実施形態を示す図である。It is a figure which shows the 13th Embodiment of this invention. 従来の円錐ころ軸受の一例を示す図である。It is a figure which shows an example of the conventional tapered roller bearing.

符号の説明Explanation of symbols

１ 内輪
１ａ 軌道面
２ 外輪
２ａ 軌道面
３ 円錐ころ
３ａ 円錐ころの大径側端面
３ｂ 円錐ころの小径側端面
４ 保持器
４ａ 保持器ポケット
５ 鍔部
６ 鍔部
７ 逃げ溝（逃げ凹部）
８ 爪部
９，１０，１１ 突起部 DESCRIPTION OF SYMBOLS 1 Inner ring 1a Raceway surface 2 Outer ring 2a Raceway surface 3 Tapered roller 3a Large diameter side end surface of a tapered roller 3b Small diameter side end surface of a tapered roller 4 Cage 4a Cage pocket 5 Gutter part 6 Gutter part 7 Escape groove (Escape recess)
8 Nail part 9, 10, 11 Protrusion part

Claims (2)

内輪と、該内輪の外周面に形成された軌道面と対向する軌道面を有する外輪と、前記内輪の軌道面と前記外輪の軌道面との間に設けられた複数の円錐ころと、該円錐ころを収容保持する複数の保持器ポケットを有する保持器とを具備してなり、前記内輪の大径側端部に鍔部を有する円錐ころ軸受であって、
前記鍔部に形成された逃げ凹部、又は内輪端面と所定の間隔を有して位置する爪部を、前記保持器の大径側端部に有し、
前記内輪の軌道面が前記円錐ころの転動面に接触すると共に前記鍔部が前記円錐ころの端面に接触し、かつ前記保持器の中心軸が前記内輪の中心軸と一致するとき、前記爪部の内側面と、該内側面に対向する前記逃げ凹部、又は前記内輪の端面との間の軸方向隙間をａ、前記円錐ころにおいて前記逃げ凹部が設けられた側の端面と前記保持器ポケットとの間の軸方向隙間をｂ、前記爪部の外側面と前記逃げ凹部との間の軸方向隙間をｃ、前記円錐ころにおいて前記逃げ凹部が設けられた側と反対側の端面と前記保持器ポケットとの間の軸方向隙間をｄとしたとき、ａ＞ｂ、ｃ＞ｄとし、
前記内輪と前記保持器との間から軸受内に油が流入することを抑制するために、前記内輪の軌道面に対して所定の間隙を形成する突起部が、前記保持器の小径側端部に形成され、
前記内輪と前記保持器との間から軸受内に油が流入することを更に抑制するために、前記突起部が前記内輪の小径側端部の一部を覆うように形成され、
前記小径側から大径側への油の流れに抗って軸受内部への油の流入を低減するために、前記突起部の小径側の面は、回転軸に直交する方向に対して所定の角度で傾斜しており、
前記内輪大径方向に、前記爪部が逃げ凹部へ挿入しやすく、その逆方向には前記爪部が前記凹部から脱落し難い形状とし、
前記爪部は、大径側を傾斜させた楔形をなすと共に、小径側に湾曲した切り欠きが形成されたことを特徴とする円錐ころ軸受。 An inner ring; an outer ring having a raceway surface opposed to a raceway surface formed on an outer peripheral surface of the inner ring; a plurality of tapered rollers provided between the raceway surface of the inner ring and the raceway surface of the outer ring; A tapered roller bearing comprising a plurality of cage pockets for containing and holding rollers, and having a flange on the large-diameter side end of the inner ring,
A relief recess formed in the flange, or a claw portion located at a predetermined distance from the inner ring end surface, has a large diameter side end of the cage,
When the raceway surface of the inner ring is in contact with the rolling surface of the tapered roller, the flange is in contact with the end surface of the tapered roller, and the central axis of the cage coincides with the central axis of the inner ring, the claw A clearance in the axial direction between the inner side surface of the portion and the escape recess facing the inner side surface or the end surface of the inner ring, the end surface of the tapered roller on the side where the escape recess is provided, and the cage pocket B, an axial gap between the outer surface of the claw and the relief recess, c, an end surface of the tapered roller opposite to the side where the relief recess is provided, and the holding A> b, c> d, where d is the axial clearance between the device pocket and
In order to prevent oil from flowing into the bearing from between the inner ring and the cage, a protrusion that forms a predetermined gap with respect to the raceway surface of the inner ring is a small diameter side end of the cage. It is formed on,
In order to further suppress the oil from flowing into the bearing from between the inner ring and the cage, the protrusion is formed so as to cover a part of the small diameter side end of the inner ring,
In order to reduce the inflow of oil into the bearing against the flow of oil from the small-diameter side to the large-diameter side, the surface on the small-diameter side of the protruding portion has a predetermined direction with respect to the direction orthogonal to the rotation axis. Inclined at an angle,
In the inner ring large-diameter direction, the claw portion is easy to insert into the escape recess, and in the opposite direction, the claw portion does not easily fall out of the recess,
A tapered roller bearing characterized in that the claw portion has a wedge shape in which the large-diameter side is inclined and a notch curved to the small-diameter side is formed . 前記保持器が樹脂製保持器であることを特徴とする請求項１に記載の円錐ころ軸受。 The tapered roller bearing according to claim 1, wherein the cage is a resin cage .
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JP2014009709A (en) * 2012-06-27 2014-01-20 Nsk Ltd Tapered roller bearing
US9151328B2 (en) 2013-10-10 2015-10-06 Jtekt Corporation Conical roller bearing
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FR3029246B1 (en) * 2014-12-01 2017-06-09 Ntn-Snr Roulements CAGE FOR SPHERICAL ROLLER BEARING COMPRISING A DEFLECTOR, BEARING COMPRISING SUCH A CAGE AND METHOD FOR ASSEMBLING SUCH A BEARING
JP2020060275A (en) * 2018-10-12 2020-04-16 株式会社ジェイテクト Conical bearing

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US4136916A (en) * 1977-06-27 1979-01-30 The Timken Company Unitized single row tapered roller bearing
JPS607423U (en) * 1983-06-28 1985-01-19 光洋精工株式会社 tapered roller bearing
JPS6333027U (en) * 1986-08-20 1988-03-03
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