JP2012047201A - Tapered roller bearing - Google Patents

Tapered roller bearing Download PDF

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Publication number
JP2012047201A
JP2012047201A JP2010187511A JP2010187511A JP2012047201A JP 2012047201 A JP2012047201 A JP 2012047201A JP 2010187511 A JP2010187511 A JP 2010187511A JP 2010187511 A JP2010187511 A JP 2010187511A JP 2012047201 A JP2012047201 A JP 2012047201A
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Prior art keywords
tapered roller
inner ring
diameter side
small
cage
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Japanese (ja)
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Yoshinori Maeda
吉則 前田
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NSK Ltd
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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
    • F16C19/00—Bearings with rolling contact, for exclusively rotary movement
    • F16C19/22—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings
    • F16C19/34—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load
    • F16C19/36—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load with a single row of rollers
    • F16C19/364—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load with a single row of rollers with tapered rollers, i.e. rollers having essentially the shape of a truncated cone
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/30—Parts of ball or roller bearings
    • F16C33/34—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
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/30—Parts of ball or roller bearings
    • F16C33/58—Raceways; Race rings
    • F16C33/583—Details of specific parts of races
    • F16C33/585—Details of specific parts of races of raceways, e.g. ribs to guide 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
    • F16C43/00—Assembling bearings
    • F16C43/04—Assembling rolling-contact bearings
    • F16C43/06—Placing rolling bodies in cages or bearings

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

Abstract

PROBLEM TO BE SOLVED: To provide a tapered roller bearing capable of preventing damage of a retainer when installing an inner ring in the retainer for holding a tapered roller, and capable of preventing the tapered roller and the retainer from separating from the inner ring, while maintaining strength of a column part.SOLUTION: This tapered roller bearing includes the inner ring having a tapered inner ring raceway surface 1s and having a small collar part 11 on the small diameter side of the inner ring raceway surface 1s and a large collar part 12 on the large diameter side, a plurality of tapered rollers 3 rollingly arranged between an outer ring raceway surface of an outer ring and the inner ring raceway surface 1s and connecting a small diameter side end surface 31 and a rolling surface 33 via a chamfering part, and the retainer 4 for holding the tapered roller 3 at a predetermined interval in the circumferential direction, wherein a plurality of tapered rollers 3 are incorporated into the inner ring 1 together with the retainer 4 by allowing the chamfering part 34 of the tapered roller 3 held by the retainer 4 to get over the small collar part 11. The chamfering part 34 of the tapered roller 3 is constituted by reducing a chamfering dimension dx3 of the small diameter side end surface 31 more than a chamfering dimension dy3 of the rolling surface 33.

Description

本発明は、建設機械、自動車、鉄道車両、その他の産業機械における回転部に使用される円すいころ軸受に関する。   The present invention relates to a tapered roller bearing used for a rotating part in a construction machine, an automobile, a railway vehicle, and other industrial machines.

従来、建設機械をはじめとする各種の駆動装置には、その回転機構を回転自在に支持する軸受として円すいころ軸受が使用されている。この円すいころ軸受は、図５（ｃ）に示すように、円すい状の外輪軌道面２ｓを有する外輪２と、円すい状の内輪軌道面１ｓを有し、該内輪軌道面１ｓの小径側に小鍔部１１、大径側に大鍔部１２を有する内輪１と、外輪軌道面２ｓと内輪軌道面１ｓとの間に転動自在に配され、小径側端面３１と転動面３３との間に面取り（以下、面取り部３４と呼ぶ。）が施された複数の円すいころ３と、円すいころ３を円周方向で所定間隔に保持する保持器４と、を備えて構成される。   2. Description of the Related Art Conventionally, tapered roller bearings are used as bearings that rotatably support a rotating mechanism in various drive devices including construction machines. As shown in FIG. 5C, this tapered roller bearing has an outer ring 2 having a conical outer ring raceway surface 2s and a conical inner ring raceway surface 1s, and a small diameter on the small diameter side of the inner ring raceway surface 1s. Between the inner ring 1 having the collar 11 and the large collar 12 on the large diameter side, and between the outer ring raceway surface 2 s and the inner ring raceway surface 1 s, it is movably arranged, and between the small diameter side end surface 31 and the rolling surface 33. And a plurality of tapered rollers 3 that are chamfered (hereinafter referred to as a chamfered portion 34), and a retainer 4 that holds the tapered rollers 3 at predetermined intervals in the circumferential direction.

円すいころ軸受の保持器は金属製であることが一般的であり、金属性保持器を用いた円すいころ軸受の組立て方法は、図４に示すように、先ず保持器４のポケット４１に円すいころ３を保持させ、内輪１に組み込む。そして、保持器加締め治具５を用いて該治具５を押し込み、内輪１及び円すいころ３、保持器４が分離しない任意のポケット隙間になるまで加締める、といった方法（いわゆる加締め方式）が採られる。   The cage of the tapered roller bearing is generally made of metal, and the method of assembling the tapered roller bearing using the metallic cage is to first insert the tapered roller into the pocket 41 of the cage 4 as shown in FIG. 3 is held and incorporated in the inner ring 1. And the method of pushing in this jig | tool 5 using the cage | basket | tool crimping jig | tool 5, and crimping until it becomes the arbitrary pocket clearance gaps which the inner ring | wheel 1, the tapered roller 3, and the holder | retainer 4 do not isolate | separate (a so-called caulking system). Is taken.

しかしながら、金属製保持器は、平板を何度も塑性変形させて製作するため、樹脂製保持器に比べ加工工程が多く、材料費が高く、重量も重いというデメリットがある。そのため、自動車向けなどの外径１００ｍｍ以下の円すいころ軸受には樹脂製保持器が多く採用されている。   However, since the metal cage is manufactured by plastically deforming a flat plate many times, there are disadvantages in that the number of processing steps is higher, the material cost is higher, and the weight is heavier than that of a resin cage. Therefore, many resin cages are used for tapered roller bearings having an outer diameter of 100 mm or less for automobiles and the like.

樹脂製保持器を用いた円すいころ軸受の組立て方法は、先ず所定のポケット隙間が残るように射出成型した保持器４のポケット４１に円すいころ３を保持させる。その後、図５（ａ）に示すように、円すいころ３を保持した保持器４に内輪１を保持器４の大径側から小径側に向かって押し込むことによって、円すいころ３がポケット４１を一時的に押し広げ、面取り部３４が内輪１の小鍔部１１を乗り越えることで、内輪１に組み込まれる（図５（ｂ））。   In the method of assembling the tapered roller bearing using the resin cage, the tapered roller 3 is first held in the pocket 41 of the cage 4 which is injection molded so that a predetermined pocket gap remains. Thereafter, as shown in FIG. 5A, the inner ring 1 is pushed into the cage 4 holding the tapered roller 3 from the larger diameter side to the smaller diameter side of the cage 4, so that the tapered roller 3 temporarily holds the pocket 41. The chamfered portion 34 gets over the small collar portion 11 of the inner ring 1 and is incorporated into the inner ring 1 (FIG. 5B).

しかしながら、当該組立て方法（いわゆる圧入方式）では、内輪１を押し込む際に保持器４の弾性変形を伴うため、保持器４が破損する可能性がある。特に、建設機械用に用いられる外径２００ｍｍ以上のサイズの大きい軸受では、保持器４の寸法のばらつきが大きくなり、保持器４が破損する可能性がより高くなる。   However, in the assembling method (so-called press-fitting method), the retainer 4 may be damaged because the retainer 4 is elastically deformed when the inner ring 1 is pushed. In particular, in a large bearing having an outer diameter of 200 mm or more used for construction machinery, the variation in the dimensions of the cage 4 becomes large, and the possibility that the cage 4 is damaged becomes higher.

組立て時の保持器破損を防止するためには、樹脂製の保持器４を変形させずに組立てるため、内輪１の小鍔部１１の外径を小さくすることが考えられる。   In order to prevent breakage of the cage during assembly, it is conceivable to reduce the outer diameter of the small flange portion 11 of the inner ring 1 in order to assemble without deforming the resin cage 4.

また、例えば特許文献１のように、樹脂製の保持器の小径側の柱部に切り欠き部を設けることによって、組立て時の保持器破損の可能性を軽減することも考えられる。   Further, for example, as in Patent Document 1, it is conceivable to reduce the possibility of breakage of the cage during assembly by providing a notch in the column portion on the small diameter side of the resin cage.

特開２００７−２７０８７４号公報JP 2007-270874 A

しかしながら、内輪１の小鍔部１１の外径を小さくすると、外輪２を外した状態で、内輪１及び円すいころ３、保持器４を製品（シャフト等）に固定する際に、内輪１から円すいころ３が分離してしまい、円すいころ３に傷がついて軸受の機能を損なったり、円すいころ３と保持器４が分離してしまい再度組立てを行うこととなり、作業性を著しく低下させてしまうおそれがある。また、特許文献１に記載の円すいころ軸受においては、保持器の柱部が部分的に細くなるため応力集中が発生しやすく、軸受使用中に保持器の切り欠き部に繰り返し応力が発生し、切り欠き部から破損するおそれがある。   However, when the outer diameter of the small flange portion 11 of the inner ring 1 is reduced, the inner ring 1 is tapered from the inner ring 1 when the inner ring 1, the tapered roller 3, and the cage 4 are fixed to a product (shaft or the like) with the outer ring 2 removed. The roller 3 may be separated, and the tapered roller 3 may be damaged to impair the function of the bearing, or the tapered roller 3 and the cage 4 may be separated and reassembled, resulting in a significant decrease in workability. There is. Moreover, in the tapered roller bearing described in Patent Document 1, stress concentration is likely to occur because the pillar portion of the cage is partially thin, and repeated stress is generated in the notch portion of the cage during use of the bearing. There is a risk of damage from the notch.

本発明は、柱部の強度に影響を与えることなく、円すいころを保持した保持器に内輪を組み付ける際に保持器の破損を防止可能、且つ、円すいころを保持した保持器に内輪を組み付けた状態では内輪から円すいころと保持器が分離するのを防止可能な円すいころ軸受を提供することにある。   The present invention can prevent damage to the cage when assembling the inner ring to the cage holding the tapered roller without affecting the strength of the pillar portion, and the inner ring is assembled to the cage holding the tapered roller. It is an object of the present invention to provide a tapered roller bearing capable of preventing the tapered roller and the cage from being separated from the inner ring.

上記目的は以下の構成により達成される。
（１）円すい状の外輪軌道面を有する外輪と、
円すい状の内輪軌道面を有し、該内輪軌道面の小径側に小鍔部、大径側に大鍔部を有する内輪と、
前記外輪軌道面と前記内輪軌道面との間に転動自在に配され、小径側端面と転動面とが面取り部を介して連結された複数の円すいころと、
前記円すいころを円周方向で所定間隔に保持する保持器と、を備え、
前記保持器に保持された前記円すいころの前記面取り部が前記小鍔部を乗り越えることにより、前記保持器と共に前記複数の円すいころが前記内輪に組み込まれる円すいころ軸受であって、
前記円すいころの面取り部が、前記転動面の面取り寸法よりも前記小径側端面の面取り寸法を小さくすることにより構成されることを特徴とする円すいころ軸受。
（２）前記保持器は、樹脂製であることを特徴とする（１）に記載の円すいころ軸受。
（３）建設機械の減速機用であることを特徴とする（１）又は（２）に記載の円すいころ軸受。
（４）外径が２００ｍｍ以上であることを特徴とする（１）〜（３）のいずれかに記載の円すいころ軸受。 The above object is achieved by the following configuration.
(1) an outer ring having a conical outer ring raceway surface;
An inner ring having a conical inner ring raceway surface, a small collar portion on the small diameter side of the inner ring raceway surface, and a large collar portion on the large diameter side;
A plurality of tapered rollers arranged between the outer ring raceway surface and the inner ring raceway surface so as to be freely rollable and having a small-diameter side end face and a rolling face connected via a chamfer;
A retainer for holding the tapered rollers at a predetermined interval in the circumferential direction,
A tapered roller bearing in which the plurality of tapered rollers are incorporated into the inner ring together with the cage when the chamfered portion of the tapered roller held by the cage gets over the small collar portion,
A tapered roller bearing, wherein the chamfered portion of the tapered roller is configured by making a chamfer dimension of the end surface on the small diameter side smaller than a chamfer dimension of the rolling surface.
(2) The tapered roller bearing according to (1), wherein the cage is made of resin.
(3) The tapered roller bearing according to (1) or (2), wherein the tapered roller bearing is used for a reduction gear of a construction machine.
(4) The tapered roller bearing according to any one of (1) to (3), wherein an outer diameter is 200 mm or more.

上記のように構成された本発明の円すいころ軸受によれば、円すいころの面取り部を、転動面の面取り寸法よりも小径側端面の面取り寸法を小さくすることにより構成したことで、柱部の強度に影響を与えることなく、円すいころを保持した保持器に内輪を組み付ける際に、面取り部が内輪の小鍔部を案内することにより保持器の破損が防止され、且つ、円すいころを保持した保持器に内輪を組み付けた状態では、小径側端面が内輪の小鍔部に干渉することにより内輪から円すいころと保持器が分離するのを防止することができる。   According to the tapered roller bearing of the present invention configured as described above, the chamfered portion of the tapered roller is configured by making the chamfer dimension of the end surface on the small diameter side smaller than the chamfer dimension of the rolling surface. When assembling the inner ring to the cage that holds the tapered roller without affecting the strength of the cage, the chamfered portion guides the small collar part of the inner ring, preventing the cage from being damaged and holding the tapered roller. In a state where the inner ring is assembled to the cage, it is possible to prevent the tapered roller and the cage from being separated from the inner ring by the small-diameter side end surface interfering with the small collar portion of the inner ring.

（ａ）は円すいころを保持した保持器に内輪を組み付け、外輪を外した状態で軸芯が鉛直方向となるように配置した本発明の一実施形態の円すいころ軸受の断面図であり、（ｂ）は（ａ）の一点鎖線で囲まれた部分の拡大図である。(A) is a cross-sectional view of a tapered roller bearing according to an embodiment of the present invention in which an inner ring is assembled to a cage holding a tapered roller and the shaft core is arranged in a vertical direction with the outer ring removed. FIG. 7B is an enlarged view of a portion surrounded by an alternate long and short dash line in FIG. （ａ）は円すいころを保持した保持器に内輪を組み付け、外輪を外した状態で軸芯が水平方向となるように配置した本発明の一実施形態の円すいころ軸受の断面図であり、（ｂ）は（ａ）の一点鎖線で囲まれた部分の拡大図である。(A) is a cross-sectional view of a tapered roller bearing according to an embodiment of the present invention in which an inner ring is assembled to a cage holding a tapered roller and the shaft core is disposed in a horizontal direction with the outer ring removed. FIG. 7B is an enlarged view of a portion surrounded by an alternate long and short dash line in FIG. 変形例の円すいころ軸受の円すいころの部分拡大図である。It is the elements on larger scale of the tapered roller of the tapered roller bearing of a modification. 金属製保持器を備える円すいころ軸受における、内輪に円すいころを保持した保持器を組み付ける方法を説明する説明図である。It is explanatory drawing explaining the method to assemble | attach the retainer which hold | maintained the tapered roller to the inner ring | wheel in a tapered roller bearing provided with metal cages. （ａ）は 樹脂製保持器を備える円すいころ軸受における、円すいころを保持した保持器に内輪を組み付ける途中の断面図であり、（ｂ）は円すいころを保持した保持器に内輪を組み付けた状態の断面図であり、（ｃ）は（ｂ）にさらに外輪を組み付けた状態の断面図である。(A) is sectional drawing in the middle of assembling an inner ring | wheel to the holder | retainer holding the tapered roller in the tapered roller bearing provided with a resin cage, (b) is the state which assembled | attached the inner ring | wheel to the holder holding the tapered roller (C) is a cross-sectional view of a state in which an outer ring is further assembled to (b). （ａ）は組み付け時に保持器を破損せずに圧入できる限界の干渉量となるような四半円弧で面取り部が構成された円すいころ軸受を、外輪を外して軸芯が鉛直方向となるように配置した状態の断面図であり、（ｂ）は（ａ）の一点鎖線で囲まれた部分の拡大図である。(A) shows a tapered roller bearing with a chamfered part formed of a semicircular arc that has a limit of interference that can be press-fitted without damaging the cage during assembly so that the outer ring is removed and the shaft core is in the vertical direction. It is sectional drawing of the state arrange | positioned, (b) is an enlarged view of the part enclosed with the dashed-dotted line of (a). 図６（ａ）に示す円すいころ軸受を軸芯が水平方向となるように配置した図であり、（ｂ）は（ａ）の一点鎖線で囲まれた部分の拡大図である。It is the figure which has arrange | positioned the tapered roller bearing shown to Fig.6 (a) so that an axial center may become a horizontal direction, (b) is an enlarged view of the part enclosed with the dashed-dotted line of (a). 内輪から保持器と円すいころが分離しない最小の干渉量となるような四半円弧で面取り部が構成された円すいころ軸受を、外輪を外して軸芯が水平方向となるように配置した状態の部分拡大図である。A part in which the tapered roller bearing with a chamfered part formed of a quarter arc so that the cage and tapered roller do not separate from the inner ring is arranged with the outer ring removed and the shaft core in the horizontal direction. It is an enlarged view. 図８に示す円すいころ軸受を軸芯が鉛直方向に配置した状態の部分拡大図である。It is the elements on larger scale in the state where the axial center has arrange | positioned the tapered roller bearing shown in FIG.

以下、本発明の円すいころ軸受の実施形態について図面を参照しながら説明する。なお、本実施形態の円すいころ軸受は、図５（ｃ）に示す円すいころ軸受と基本的構成を同一にするので、先ず図５（ｃ）を参照して、本実施形態の円すいころ軸受の基本的構成について説明する。また、図面は符号の向きに見るものとする。   Hereinafter, embodiments of the tapered roller bearing of the present invention will be described with reference to the drawings. The tapered roller bearing of the present embodiment has the same basic configuration as that of the tapered roller bearing shown in FIG. 5C. First, referring to FIG. 5C, the tapered roller bearing of the present embodiment. A basic configuration will be described. The drawings are to be viewed in the direction of the reference numerals.

本実施形態の円すいころ軸受は、図５（ｃ）に示すように、円すい状の外輪軌道面２ｓを有する外輪２と、円すい状の内輪軌道面１ｓを有し、該内輪軌道面１ｓの小径側に小鍔部１１、大径側に大鍔部１２を有する内輪１と、外輪軌道面２ｓと内輪軌道面１ｓとの間に転動自在に配された複数の円すいころ３と、円すいころ３を円周方向で所定間隔に保持する保持器４と、を備えて構成される。   As shown in FIG. 5 (c), the tapered roller bearing of the present embodiment has an outer ring 2 having a tapered outer ring raceway surface 2s, and a tapered inner ring raceway surface 1s, and the inner ring raceway surface 1s has a small diameter. An inner ring 1 having a small flange portion 11 on the side and a large flange portion 12 on the large diameter side, a plurality of tapered rollers 3 disposed so as to roll between the outer ring raceway surface 2s and the inner ring raceway surface 1s, and a tapered roller. And a retainer 4 that retains 3 at a predetermined interval in the circumferential direction.

保持器４は、樹脂から構成され、小径環状部４２と、大径環状部４３と、小径環状部４２と大径環状部４３とを連結して周方向に略等間隔で配置される複数の柱部４４とを備え、これら小径環状部４２、大径環状部４３、および隣接する柱部４４とで円すいころ３を保持するポケット４１を構成する。各ポケット４１には、それぞれ円すいころ３が転動自在に保持される。   The cage 4 is made of resin, and connects the small-diameter annular portion 42, the large-diameter annular portion 43, the small-diameter annular portion 42, and the large-diameter annular portion 43, and is arranged at substantially equal intervals in the circumferential direction. The small-diameter annular portion 42, the large-diameter annular portion 43, and the adjacent pillar portion 44 constitute a pocket 41 that holds the tapered roller 3. The tapered rollers 3 are held in the respective pockets 41 so as to freely roll.

円すいころ３は、小径側端面３１と大径側端面３２が同心状に配置され、両端面を結ぶ周面が大径側端面３２側から小径側端面３１側へ向かうに従って徐々に縮径された転動面３３をなしている。小径側端面３１と転動面３３とは面取り部３４を介して連結されている。言い換えると、小径側端面３１と転動面３３との間に面取り部３４が設けられている。   In the tapered roller 3, the small-diameter side end surface 31 and the large-diameter side end surface 32 are arranged concentrically, and the circumferential surface connecting both end surfaces is gradually reduced in diameter as it goes from the large-diameter side end surface 32 side to the small-diameter side end surface 31 side. A rolling surface 33 is formed. The small diameter side end surface 31 and the rolling surface 33 are connected via a chamfered portion 34. In other words, the chamfered portion 34 is provided between the small diameter side end surface 31 and the rolling surface 33.

続いて、本発明の円すいころ軸受の特徴部分について図１及び図２を参照して説明する。
図１（ｂ）に拡大して示すように、円すいころ３の面取り部３４は、図中ｒ３で示されるように、転動面３３の面取り寸法ｄｙ３よりも小径側端面３１の面取り寸法ｄｘ３を小さくすることにより構成される。ここで、転動面３３の面取り寸法ｄｙ３とは、転動面３３と面取り部３４との境界点Ｐ３から小径側端面３１までの転動面３３に沿った距離であり、小径側端面３１の面取り寸法ｄｘ３とは、小径側端面３１と面取り部３４との境界点Ｑ３から転動面３３までの小径側端面３１に沿った距離である。 Then, the characteristic part of the tapered roller bearing of this invention is demonstrated with reference to FIG.1 and FIG.2.
As shown in an enlarged view in FIG. 1B, the chamfered portion 34 of the tapered roller 3 has a chamfered dimension dx3 of the end surface 31 on the smaller diameter side with respect to the chamfered dimension dy3 of the rolling surface 33, as indicated by r3 in the figure. It is configured by making it smaller. Here, the chamfer dimension dy3 of the rolling surface 33 is a distance along the rolling surface 33 from the boundary point P3 between the rolling surface 33 and the chamfered portion 34 to the small diameter side end surface 31, and The chamfer dimension dx3 is a distance along the small diameter side end surface 31 from the boundary point Q3 between the small diameter side end surface 31 and the chamfered portion 34 to the rolling surface 33.

通常、小径側端面３１と転動面３３との間に施される面取りは、転動面３３の面取り寸法と小径側端面３１の面取り寸法が等しくなる四半円弧で形成されるが、本発明の面取り部３４は、転動面３３の面取り寸法ｄｙ３よりも小径側端面３１の面取り寸法ｄｘ３を小さくしたものである。   Normally, the chamfering performed between the small-diameter side end surface 31 and the rolling surface 33 is formed by a quarter arc with the chamfering dimension of the rolling surface 33 equal to the chamfering dimension of the small-diameter side end surface 31. The chamfered portion 34 is obtained by making the chamfer dimension dx3 of the small-diameter side end surface 31 smaller than the chamfer dimension dy3 of the rolling surface 33.

ここで、面取り部３４を四半円弧で構成する場合について検討する。
図６（ｂ）は、面取り部３４を組み付け時の保持器４を破損せずに圧入できる限界の干渉量Ｓ１となるような四半円弧ｒ１としたものであり、転動面３３と面取り部３４との境界点Ｐ１から小径側端面３１までの転動面３３に沿った距離である転動面３３の面取り寸法ｄｙ１と、小径側端面３１と面取り部３４との境界点Ｑ１から転動面３３までの小径側端面３１に沿った距離である小径側端面３１の面取り寸法ｄｘ１は等しくなっている（ｄｙ１＝ｄｘ１）。限界の干渉量Ｓ１は、面取り部３４を構成する四半円弧ｒ１の最も内径側に位置する最内径点から小鍔部外周面１１ａまでの径方向距離であり、内輪１を円すいころ３を保持した保持器４に押し込む際の円すいころ３の径方向の移動量である。従って、図６（ａ）に示すように、円すいころ軸受の軸芯Ｏが鉛直方向となるように配置して円すいころ３を保持した保持器４に内輪１を組み付ける際には、限界の干渉量Ｓ１に基づいて転動面３３の面取り寸法ｄｙ１が設定されているので、組み付ける時の保持器４の破損が防止される。 Here, a case where the chamfered portion 34 is formed of a quarter arc is considered.
FIG. 6B shows a quadrant arc r1 that has a limit interference amount S1 that can be press-fitted without damaging the retainer 4 when the chamfer 34 is assembled. The rolling surface 33 and the chamfer 34 are shown in FIG. The chamfer dimension dy1 of the rolling surface 33, which is the distance along the rolling surface 33 from the boundary point P1 to the small diameter side end surface 31, and the rolling surface 33 from the boundary point Q1 between the small diameter side end surface 31 and the chamfered portion 34. The chamfer dimension dx1 of the small-diameter side end surface 31 that is the distance along the small-diameter side end surface 31 is equal (dy1 = dx1). The limit interference amount S1 is a radial distance from the innermost diameter point located on the innermost diameter side of the quarter arc r1 constituting the chamfered portion 34 to the outer peripheral surface 11a of the small flange portion, and the inner ring 1 holds the tapered roller 3. This is the radial movement amount of the tapered roller 3 when pushed into the cage 4. Therefore, as shown in FIG. 6 (a), when the inner ring 1 is assembled to the retainer 4 that holds the tapered roller 3 by arranging the axial center O of the tapered roller bearing in the vertical direction, there is a limit interference. Since the chamfer dimension dy1 of the rolling surface 33 is set based on the amount S1, damage to the cage 4 during assembly is prevented.

しかし、図７（ａ）に示すように、円すいころ軸受の軸芯Ｏが水平方向となるように配置して外輪２を外した状態で内輪１及び円すいころ３、保持器４をシャフト等に固定する際、主に円すいころ３の自重により鉛直方向上方では円すいころ３と内輪軌道面１ｓとの隙間がなくなり、鉛直方向下方では鉛直方向上方の隙間減少分だけ隙間が広がることとなる。それにより、図７（ｂ）に示すように、最下部に位置する円すいころ３の小径側端面３１と面取り部３４との境界点Ｑ１が小鍔部外周面１１ａよりＬ１だけ下方に位置することとなる。従って、図中矢印で示す大鍔部１２側から小鍔部１１側に力が加わると面取り部３４が小鍔部先端Ｂに接触し、円すいころ３が小鍔部先端Ｂに案内されて、内輪１から保持器４と円すいころ３が分離してしまうおそれがある。   However, as shown in FIG. 7 (a), the inner ring 1, the tapered roller 3, and the retainer 4 are attached to a shaft or the like with the outer ring 2 removed by arranging the axial center O of the tapered roller bearing in the horizontal direction. When fixing, the gap between the tapered roller 3 and the inner ring raceway surface 1 s disappears in the vertical direction mainly due to the weight of the tapered roller 3, and the gap widens by the gap decrease in the vertical direction below in the vertical direction. As a result, as shown in FIG. 7B, the boundary point Q1 between the small diameter side end surface 31 and the chamfered portion 34 of the tapered roller 3 positioned at the lowermost position is positioned below the small flange outer peripheral surface 11a by L1. It becomes. Therefore, when a force is applied from the large collar part 12 side to the small collar part 11 side indicated by an arrow in the figure, the chamfered part 34 comes into contact with the small collar part tip B, and the tapered roller 3 is guided to the small collar part tip B, There is a possibility that the cage 4 and the tapered roller 3 are separated from the inner ring 1.

これに対し、内輪１から保持器４と円すいころ３が分離してしまうのを防止するため、図８に示すように、最下部に位置する円すいころ３の小径側端面３１と面取り部３４との境界点Ｑ２が内輪１から保持器４と円すいころ３が分離しない最小の干渉量Ｌ２だけ小鍔部外周面１１ａより上方に位置するように四半円弧ｒ２を設定した場合を考える。このとき、転動面３３と面取り部３４との境界点Ｐ２から小径側端面３１までの転動面３３に沿った距離である転動面３３の面取り寸法ｄｙ２と、小径側端面３１と面取り部３４との境界点Ｑ２から転動面３３までの小径側端面３１に沿った距離である小径側端面３１の面取り寸法ｄｘ２は等しくなっており、ｄｘ２＜ｄｘ１、ｄｙ２＜ｄｙ１の関係となっている。これにより、図中矢印で示す大鍔部１２側から小鍔部１１側に力が加わっても、面取り部３４が小鍔部先端Ｂに接触して矢印方向の移動が規制され、内輪１から保持器４と円すいころ３が分離してしまうのが防止される。   On the other hand, in order to prevent the retainer 4 and the tapered roller 3 from separating from the inner ring 1, as shown in FIG. 8, the small-diameter side end surface 31 and the chamfered portion 34 of the tapered roller 3 located at the lowermost part Let us consider a case where the quadrant arc r2 is set so that the boundary point Q2 is positioned above the small flange outer peripheral surface 11a by a minimum interference amount L2 at which the retainer 4 and the tapered roller 3 are not separated from the inner ring 1. At this time, the chamfer dimension dy2 of the rolling surface 33, which is the distance along the rolling surface 33 from the boundary point P2 between the rolling surface 33 and the chamfered portion 34 to the small diameter side end surface 31, the small diameter side end surface 31 and the chamfered portion. 34, the chamfer dimension dx2 of the small diameter side end surface 31 which is the distance along the small diameter side end surface 31 from the boundary point Q2 to the rolling surface 33 is equal, and the relationship of dx2 <dx1, dy2 <dy1 is established. . As a result, even if a force is applied from the side of the large collar portion 12 indicated by the arrow to the side of the small collar portion 11, the chamfered portion 34 comes into contact with the distal end B of the small collar portion and movement in the direction of the arrow is restricted. The cage 4 and the tapered roller 3 are prevented from separating.

しかし、この場合、円すいころ軸受の軸芯Ｏが鉛直方向となるように配置して円すいころ３を保持した保持器４に内輪１を組み付ける際には、図９に示すように、四半円弧ｒ２の最も内径側に位置する最内径点から小鍔部外周面１１ａまでの径方向距離Ｓ２が限界の干渉量Ｓ１より長くなるので、組み付け時に保持器４が破損するおそれがある。   However, in this case, when the inner ring 1 is assembled to the retainer 4 that holds the tapered roller 3 and is arranged so that the axis O of the tapered roller bearing is in the vertical direction, as shown in FIG. Since the radial distance S2 from the innermost diameter point located on the innermost diameter side to the small flange outer peripheral surface 11a is longer than the limit interference amount S1, the cage 4 may be damaged during assembly.

従って、本実施形態では、図１（ｂ）及び図２（ｂ）に示すように、面取り部３４における小径側端面３１の面取り寸法ｄｘ３を、内輪１から保持器４と円すいころ３が分離しない最大寸法ｄｘ２以下とし（ｄｘ３≦ｄｘ２）、且つ、転動面３３の面取り寸法ｄｙ３を、円すいころ３を保持した保持器４に内輪１を組み付ける際に保持器４が破損しない最小寸法ｄｙ１以上としている（ｄｙ３≧ｄｙ１）。   Therefore, in this embodiment, as shown in FIGS. 1B and 2B, the cage 4 and the tapered roller 3 do not separate the chamfer dimension dx3 of the small diameter side end surface 31 in the chamfered portion 34 from the inner ring 1. The maximum dimension dx2 or less (dx3 ≦ dx2), and the chamfering dimension dy3 of the rolling surface 33 is set to a minimum dimension dy1 or more that does not damage the cage 4 when the inner ring 1 is assembled to the cage 4 holding the tapered roller 3. (Dy3 ≧ dy1).

これにより、図１（ａ）に示すように、円すいころ軸受の軸芯Ｏが鉛直方向となるように配置して円すいころ３を保持した保持器４に内輪１を組み付ける際には、図１（ｂ）に示すように、面取り部３４を構成する面取りｒ３の最も内径側に位置する最内径点から小鍔部外周面１１ａまでの径方向距離Ｓ３が限界干渉量Ｓ１以下となる。従って、面取り部３４が内輪１の小鍔部先端Ｂを案内することにより、組み付け時に円すいころ３がポケット４１を一時的に押し広げ、円すいころ３の面取り部３４が内輪１の小鍔部１１を乗り越えて、内輪１に組み込まれて、組み付け時の保持器４の破損が防止される。   As a result, as shown in FIG. 1A, when the inner ring 1 is assembled to the retainer 4 that holds the tapered roller 3 by arranging the axis O of the tapered roller bearing in the vertical direction, As shown in FIG. 5B, the radial distance S3 from the innermost diameter point located on the innermost diameter side of the chamfering r3 constituting the chamfered portion 34 to the outer peripheral surface 11a of the small flange portion is equal to or less than the limit interference amount S1. Accordingly, the chamfered portion 34 guides the tip B of the inner ring 1 so that the tapered roller 3 temporarily spreads the pocket 41 during the assembly, and the chamfered portion 34 of the tapered roller 3 becomes the gavel portion 11 of the inner ring 1. The cage 4 is assembled into the inner ring 1 to prevent breakage of the cage 4 during assembly.

また、図２（ａ）に示すように、円すいころ３を保持した保持器４に内輪１を組み付け、外輪２を外した状態で軸芯Ｏが水平方向になるように配置して内輪１及び円すいころ３、保持器４をシャフト等に固定する際には、図２（ｂ）に示すように、最下部に位置する円すいころ３の小径側端面３１と面取り部３４との境界点Ｑ３から小鍔部外周面１１ａまでの径方向距離Ｌ３が分離しない最小の干渉量Ｌ２以上となる。従って、この状態で大鍔部１２側から小鍔部１１側に力が加わったとしても、小径側端面３１が内輪１の小鍔部先端Ｂに干渉することにより内輪１から円すいころ３と保持器４が分離するのを防止することができる。   Further, as shown in FIG. 2A, the inner ring 1 is assembled to the cage 4 holding the tapered rollers 3, and the outer ring 2 is removed so that the shaft core O is in the horizontal direction. When fixing the tapered roller 3 and the cage 4 to a shaft or the like, as shown in FIG. 2B, from the boundary point Q3 between the small-diameter side end surface 31 and the chamfered portion 34 of the tapered roller 3 positioned at the bottom. The radial distance L3 to the small collar outer peripheral surface 11a is not less than the minimum interference amount L2 that is not separated. Therefore, even if a force is applied from the large collar part 12 side to the small collar part 11 side in this state, the small diameter side end surface 31 interferes with the small collar part tip B of the inner ring 1 so that the inner ring 1 holds the tapered roller 3. The container 4 can be prevented from separating.

以上説明したように、本実施形態の円すいころ軸受によれば、面取り部３４が、転動面３３の面取り寸法ｄｙ３よりも小径側端面３１の面取り寸法ｄｘ３を小さくすることにより構成されることで、柱部４４の強度に影響を与えることなく、円すいころ３を保持した保持器４に内輪１を組み付ける際に、面取り部３４が内輪１の小鍔部１１を案内することにより保持器４の破損が防止され、且つ、円すいころ３を保持した保持器４に内輪１を組み付けた状態では、小径側端面３１が内輪１の小鍔部１１に干渉することにより内輪１から円すいころ３と保持器４が分離するのを防止することができる。また、本発明は、外径が２００ｍｍ以上の円すいころ軸受に特に有用であり、建設機械の減速機用に好適に用いられる。   As described above, according to the tapered roller bearing of the present embodiment, the chamfered portion 34 is configured by making the chamfer dimension dx3 of the small diameter side end surface 31 smaller than the chamfer dimension dy3 of the rolling surface 33. When the inner ring 1 is assembled to the retainer 4 that holds the tapered roller 3 without affecting the strength of the pillar portion 44, the chamfered portion 34 guides the small collar portion 11 of the inner ring 1, thereby In a state where the inner ring 1 is assembled to the cage 4 that holds the tapered roller 3 and is prevented from being damaged, the small diameter side end face 31 interferes with the small flange portion 11 of the inner ring 1 so that the inner ring 1 holds the tapered roller 3. The container 4 can be prevented from separating. Further, the present invention is particularly useful for a tapered roller bearing having an outer diameter of 200 mm or more, and is suitably used for a reduction gear of a construction machine.

なお、本発明に係る複列転がり軸受は、上記実施形態に限定されるものではなく、本発明の趣旨を逸脱しなければ種々の変形が可能である。
例えば、図３に示すように、転動面３３の面取り寸法ｄｙ３を組み付け時に保持器４が破損しない最小寸法ｄｙ１以上、且つ、小径側端面３１の面取り寸法ｄｘ３を内輪１から保持器４と円すいころ３が分離しない最大寸法ｄｘ２以下とすれば、円すいころ３の面取り部３４はテーパー形状であってもよい。 The double row rolling bearing according to the present invention is not limited to the above embodiment, and various modifications can be made without departing from the gist of the present invention.
For example, as shown in FIG. 3, the chamfer dimension dy3 of the rolling surface 33 is equal to or larger than the minimum dimension dy1 at which the retainer 4 is not damaged at the time of assembly, and the chamfer dimension dx3 of the small-diameter side end surface 31 is from the inner ring 1 to the retainer 4 and the cone. The chamfered portion 34 of the tapered roller 3 may have a tapered shape as long as the maximum dimension dx2 at which the roller 3 is not separated is equal to or less.

また、面取りの形状はテーパー形状以外でも、複数の円弧（アール）で構成される面取りや、複数のテーパーで構成される面取り、単数又は複数のテーパー及びアールの組合せで構成される面取りであってもよい。   Further, the chamfered shape may be a chamfer constituted by a plurality of arcs (R), a chamfer constituted by a plurality of tapers, or a chamfer constituted by a combination of one or a plurality of tapers and a radius, other than the tapered shape. Also good.

なお、金属製保持器が採用された円すいころ軸受においても、本発明の面取りを設けたころが採用された場合、加締め不良等による組み付け後の軸受分離防止の効果を得ることができ、本発明は樹脂製保持器に限らず金属製保持器にも適用することができる。   Even in a tapered roller bearing using a metal cage, when the roller provided with the chamfer of the present invention is used, it is possible to obtain an effect of preventing the bearing from being separated after assembly due to a caulking defect, etc. The invention can be applied not only to a resin cage but also to a metal cage.

１ 内輪
１１ 小鍔部
１２ 大鍔部
１ｓ 内輪軌道面
２ 外輪
２ｓ 外輪軌道面
３ 円すいころ
３１ 小径側端面
３２ 大径側端面
３３ 転動面
３４ 面取り部
４ 保持器
ｄｙ３ 転動面の面取り寸法
ｄｘ３ 小径側端面の面取り寸法 DESCRIPTION OF SYMBOLS 1 Inner ring 11 Small collar part 12 Large collar part 1s Inner ring raceway surface 2 Outer ring 2s Outer ring raceway surface 3 Tapered roller 31 Small diameter side end surface 32 Large diameter side end surface 33 Rolling surface 34 Chamfered part 4 Cage dy3 Chamfering dimension dx3 of rolling surface Chamfer dimension of small diameter end face

Claims (4)

円すい状の外輪軌道面を有する外輪と、
円すい状の内輪軌道面を有し、該内輪軌道面の小径側に小鍔部、大径側に大鍔部を有する内輪と、
前記外輪軌道面と前記内輪軌道面との間に転動自在に配され、小径側端面と転動面とが面取り部を介して連結された複数の円すいころと、
前記円すいころを円周方向で所定間隔に保持する保持器と、を備え、
前記保持器に保持された前記円すいころの前記面取り部が前記小鍔部を乗り越えることにより、前記保持器と共に前記複数の円すいころが前記内輪に組み込まれる円すいころ軸受であって、
前記円すいころの面取り部が、前記転動面の面取り寸法よりも前記小径側端面の面取り寸法を小さくすることにより構成されることを特徴とする円すいころ軸受。 An outer ring having a conical outer ring raceway surface;
An inner ring having a conical inner ring raceway surface, a small collar portion on the small diameter side of the inner ring raceway surface, and a large collar portion on the large diameter side;
A plurality of tapered rollers arranged between the outer ring raceway surface and the inner ring raceway surface so as to be freely rollable and having a small-diameter side end face and a rolling face connected via a chamfer;
A retainer for holding the tapered rollers at a predetermined interval in the circumferential direction,
A tapered roller bearing in which the plurality of tapered rollers are incorporated into the inner ring together with the cage when the chamfered portion of the tapered roller held by the cage gets over the small collar portion,
A tapered roller bearing, wherein the chamfered portion of the tapered roller is configured by making a chamfer dimension of the end surface on the small diameter side smaller than a chamfer dimension of the rolling surface. 前記保持器は、樹脂製であることを特徴とする請求項１に記載の円すいころ軸受。   The tapered roller bearing according to claim 1, wherein the cage is made of resin. 建設機械の減速機用であることを特徴とする請求項１又は２に記載の円すいころ軸受。   The tapered roller bearing according to claim 1 or 2, wherein the tapered roller bearing is used for a reduction gear of a construction machine. 外径が２００ｍｍ以上であることを特徴とする請求項１〜３のいずれか１項に記載の円すいころ軸受。   The tapered roller bearing according to any one of claims 1 to 3, wherein an outer diameter is 200 mm or more.
JP2010187511A 2010-08-24 2010-08-24 Tapered roller bearing Pending JP2012047201A (en)

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Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2014228136A (en) * 2013-05-27 2014-12-08 日本精工株式会社 Conical roller bearing

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2014228136A (en) * 2013-05-27 2014-12-08 日本精工株式会社 Conical roller bearing

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