JP2009210078A - Self-aligning roller bearing - Google Patents

Self-aligning roller bearing Download PDF

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Publication number
JP2009210078A
JP2009210078A JP2008055658A JP2008055658A JP2009210078A JP 2009210078 A JP2009210078 A JP 2009210078A JP 2008055658 A JP2008055658 A JP 2008055658A JP 2008055658 A JP2008055658 A JP 2008055658A JP 2009210078 A JP2009210078 A JP 2009210078A
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self
roller bearing
spherical
aligning roller
rollers
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Japanese (ja)
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Yohei Kashiwakura
洋平 柏倉
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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
    • 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
    • F16C33/4688—Cages for rollers or needles with rolling elements with smaller diameter than the load carrying rollers, e.g. cages with counter-rotating spacers
    • 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
    • F16C23/00—Bearings for exclusively rotary movement adjustable for aligning or positioning
    • F16C23/06—Ball or roller bearings
    • F16C23/08—Ball or roller bearings self-adjusting
    • F16C23/082—Ball or roller bearings self-adjusting by means of at least one substantially spherical surface
    • F16C23/086—Ball or roller bearings self-adjusting by means of at least one substantially spherical surface forming a track for rolling elements
    • 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
    • F16C33/37—Loose spacing bodies
    • 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
    • F16C33/60—Raceways; Race rings divided or split, e.g. comprising two juxtaposed rings
    • F16C33/605—Raceways; Race rings divided or split, e.g. comprising two juxtaposed rings with a separate retaining member, e.g. flange, shoulder, guide ring, secured to a race ring, adjacent to the race surface, so as to abut the end of the rolling elements, e.g. rollers, or the cage
    • 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
    • F16C19/02—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows
    • F16C19/10—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for axial load mainly
    • 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
    • F16C19/30—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 axial load mainly
    • 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
    • F16C19/38—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 two or more rows of rollers

Abstract

<P>PROBLEM TO BE SOLVED: To provide a self-aligning roller bearing having construction for effectively preventing heating, wear and seizure inside the bearing by reducing friction between each of the end faces of spherical rollers 3, 3 and each of the side faces of a guide ring. <P>SOLUTION: In annular clearances 13a, 13b between each of both side faces 12a, 12b of the guide ring 10 and each of one-end faces 18a, 18b of the spherical rollers 3, 3 opposed to the side faces 12a, 12b, the thrust tapered roller bearings 14a, 14b are provided, thus solving the above issues. <P>COPYRIGHT: (C)2009,JPO&INPIT

Description

この発明に係る自動調心ころ軸受は、各種機械装置に組み込んで、例えばハウジングの内側に回転軸を支承するのに利用する。   The self-aligning roller bearing according to the present invention is incorporated in various mechanical devices and used for supporting a rotating shaft inside a housing, for example.

例えば重量の嵩む軸をハウジングの内側に回転自在に支承する為に従来から、特許文献１〜２に記載された様な自動調心ころ軸受が使用されている。この自動調心ころ軸受は、図６〜７に示す様に、互いに同心に組み合わされた外輪１と内輪２との間に、複数の球面ころ３、３を転動自在に配列して成る。そして、１対の保持器４、４により、これら複数の球面ころ３、３の分離防止を図っている。   For example, in order to rotatably support a heavy shaft on the inside of a housing, a self-aligning roller bearing as described in Patent Documents 1 and 2 has been used. As shown in FIGS. 6 to 7, this self-aligning roller bearing is formed by rolling a plurality of spherical rollers 3 and 3 between an outer ring 1 and an inner ring 2 which are concentrically combined with each other. The pair of retainers 4 and 4 prevent separation of the plurality of spherical rollers 3 and 3.

上記外輪１の内周面には、単一の中心を有する球状凹面である外輪軌道５を形成している。又、内輪２の外周面の幅方向（図６〜７の左右方向）両側には、それぞれが上記外輪軌道５と対向する、１対の内輪軌道６、６を形成している。又、上記各球面ころ３、３は、それぞれの最大径部が軸方向中央部にある対称形で、上記外輪軌道５と上記１対の内輪軌道６、６との間に、２列に亙って転動自在に配列されている。   An outer ring raceway 5 that is a spherical concave surface having a single center is formed on the inner peripheral surface of the outer ring 1. In addition, a pair of inner ring raceways 6 and 6 are formed on both sides of the outer peripheral surface of the inner ring 2 in the width direction (left and right direction in FIGS. 6 to 7). Each of the spherical rollers 3 and 3 has a symmetrical shape in which the maximum diameter portion is in the axial center, and is arranged in two rows between the outer ring raceway 5 and the pair of inner ring raceways 6 and 6. It is arranged so that it can roll freely.

上記各保持器４、４は、図６〜７に示す様に、円錐筒状の主部７と、この主部７の小径側端縁部から直径方向内側に延びた内向フランジ部８とを有する。このうちの主部７に複数のポケット９、９を形成して、これら各ポケット９、９内にそれぞれ１個ずつの球面ころ３、３を、転動自在に保持している。
又、上記両保持器４、４の大径側端部内周面を案内リング１０の外周縁に近接させる事で、これら両保持器４、４を案内している。この案内リング１０は、上記２列に配列された複数の球面ころ３、３の間に、回転自在に設けられている。更に、この案内リング１０の両側面は、これら各球面ころ３、３の一端面に近接する事で、これら各球面ころ３、３を案内し、上記各球面ころ３、３の回転中心軸が正規の状態から傾斜する（スキューする）事を防止している。 As shown in FIGS. 6 to 7, each of the cages 4, 4 includes a conical cylindrical main portion 7 and an inward flange portion 8 extending inward in the diameter direction from the small-diameter side edge of the main portion 7. Have. A plurality of pockets 9 and 9 are formed in the main portion 7, and one spherical roller 3 and 3 is held in each of the pockets 9 and 9 so as to freely roll.
In addition, the cages 4 and 4 are guided by bringing the inner peripheral surfaces of the large diameter side end portions of the cages 4 and 4 close to the outer peripheral edge of the guide ring 10. The guide ring 10 is rotatably provided between the plurality of spherical rollers 3 and 3 arranged in the two rows. Further, both side surfaces of the guide ring 10 are close to one end surfaces of the spherical rollers 3 and 3 so that the spherical rollers 3 and 3 are guided. Inclination (skew) from the normal state is prevented.

上述の様に構成される自動調心ころ軸受により、例えばハウジングの内側に回転軸を支承する場合、外輪１をハウジングに内嵌固定し、内輪２を回転軸に外嵌固定する。回転軸と共に内輪２が回転する場合には、複数の球面ころ３、３が転動して、この回転を許容する。ハウジングの軸心と回転軸の軸心とが不一致の場合、外輪１の内側で内輪２が調心する（外輪１の中心軸に対し内輪２の中心軸を傾斜させる）事で、この不一致を補償する。この場合に於いて、外輪軌道５は単一球面状に形成されている為、上記複数の球面ころ３、３の転動は、不一致補償後に於いても、円滑に行なわれる。
ところが、上述した様な構造の自動調心ころ軸受の場合、運転時には、上記各球面ころ３、３の一端面と上記案内リング１１の両側面とが、摺接しながら相対回転する。この為、高速運転時には、摩擦による発熱や摩耗、焼付きが発生する可能性がある。 For example, when the rotating shaft is supported inside the housing by the self-aligning roller bearing configured as described above, the outer ring 1 is fitted and fixed to the housing, and the inner ring 2 is fitted and fixed to the rotating shaft. When the inner ring 2 rotates together with the rotating shaft, the plurality of spherical rollers 3 and 3 roll to allow this rotation. When the shaft center of the housing and the shaft center of the rotating shaft do not match, the inner ring 2 is aligned inside the outer ring 1 (the center axis of the inner ring 2 is inclined with respect to the center axis of the outer ring 1). To compensate. In this case, since the outer ring raceway 5 is formed in a single spherical shape, the rolling of the plurality of spherical rollers 3 and 3 is performed smoothly even after the mismatch compensation.
However, in the case of the self-aligning roller bearing having the above-described structure, during operation, one end face of each of the spherical rollers 3 and 3 and both side faces of the guide ring 11 rotate relative to each other while sliding. For this reason, during high-speed operation, heat generation, wear, and seizure may occur due to friction.

特開平８−２８５７６号公報JP-A-8-28576 特開２００１−１４０８７５号公報JP 2001-140875 A

本発明は、上述の様な事情に鑑みて、自動調心ころ軸受の運転時に、各球面ころと案内リングとの間の摩擦を低減し、この軸受内部の発熱、摩耗、焼付きを防止できる構造を実現すべく発明したものである。   In view of the circumstances as described above, the present invention reduces friction between each spherical roller and the guide ring during operation of the self-aligning roller bearing, and can prevent heat generation, wear, and seizure inside the bearing. It was invented to realize the structure.

本発明の対象となる自動調心ころ軸受は、外輪と、内輪と、複数個の球面ころと、保持器と、案内輪とを備える。
このうちの外輪は、内周面に単一の中心を有する球状凹面である外輪軌道を有する。
又、上記内輪は、外周面に上記外輪軌道と対向する１対の内輪軌道を有する。
又、上記各球面ころは、この外輪軌道とこの内輪軌道との間に、２列に亙って転動自在に設けられている。
又、上記保持器は、上記各球面ころを転動自在に保持する複数のポケットを備えた部分円すい筒状の主部を有する。
又、上記案内輪は、上記保持器の大径側端部の内周面と上記内輪との間で、上記両列の球面ころ同士の列間の環状隙間に設けられている。 A self-aligning roller bearing that is an object of the present invention includes an outer ring, an inner ring, a plurality of spherical rollers, a cage, and a guide ring.
Of these, the outer ring has an outer ring raceway which is a spherical concave surface having a single center on the inner peripheral surface.
The inner ring has a pair of inner ring raceways opposed to the outer ring raceway on the outer peripheral surface.
The spherical rollers are provided between the outer ring raceway and the inner ring raceway so as to roll in two rows.
The retainer has a partial conical cylindrical main portion having a plurality of pockets for rotatably holding the spherical rollers.
The guide wheel is provided in an annular gap between the rows of the spherical rollers of the two rows between the inner circumferential surface of the large-diameter end of the cage and the inner ring.

特に、本発明の自動調心ころ軸受に於いては、上記案内輪の軸方向両側面と、これら両側面と対向する上記各球面ころの端面との間に、複数の転動体と、これら各転動体を転動自在に、且つ、上記各球面ころ側への脱落を阻止した状態で保持する、保持器とを設けている。
又、上述の様な、本発明の自動調心ころ軸受を実施する場合に、具体的には、請求項２に記載した様に、上記転動体を円すいころとするか、或いは、請求項３に記載した様に、上記転動体を玉とする。 In particular, in the self-aligning roller bearing of the present invention, a plurality of rolling elements are provided between the axial side surfaces of the guide wheel and the end surfaces of the spherical rollers facing the both side surfaces. A cage is provided that holds the rolling element in a rollable manner and in a state in which the rolling element is prevented from falling off to the spherical roller side.
In the case of carrying out the self-aligning roller bearing of the present invention as described above, specifically, as described in claim 2, the rolling element is a tapered roller, or, As described in, the rolling element is a ball.

上述の様に構成する本発明の自動調心ころ軸受によれば、従来は滑り接触であった、案内輪の両側面と、この両側面と対向する、各球面ころの一端面との間の接触状態を、転がり接触とする事で摩擦を低減する事ができる。この為、この接触部での発熱、摩耗、焼付きを有効に防止する事ができ、自動調心ころ軸受の耐久性を向上する事ができる。   According to the self-aligning roller bearing of the present invention configured as described above, between the both side surfaces of the guide wheel and the one end surface of each spherical roller facing the both side surfaces, which has conventionally been a sliding contact. Friction can be reduced by making the contact state rolling contact. For this reason, heat generation, wear, and seizure at the contact portion can be effectively prevented, and the durability of the self-aligning roller bearing can be improved.

［実施の形態の第１例］
図１〜３は、請求項１、２に対応する、本発明の実施の形態の第１例を示している。尚、本例の特徴は、自動調心ころ軸受を構成する各球面ころ３、３の一端面１８ａ、１８ｂと案内輪１０の両側面１２ａ、１２ｂとの係合部の構造に工夫した点にある。この特徴部分以外の構造及び作用は、前述の図６、７に示した自動調心ころ軸受を含め、従来から知られている自動調心ころ軸受の場合と同様である。この為、重複する説明を省略若しくは簡略にし、以下、本例の特徴部分を中心に説明する。 [First example of embodiment]
1-3 show a first example of an embodiment of the present invention corresponding to claims 1 and 2. The feature of this example is that the structure of the engaging portion between one end face 18a, 18b of each spherical roller 3, 3 constituting the self-aligning roller bearing and both side faces 12a, 12b of the guide wheel 10 is devised. is there. The structure and operation other than this characteristic part are the same as those of the conventional self-aligning roller bearings including the self-aligning roller bearings shown in FIGS. For this reason, the overlapping description will be omitted or simplified, and the following description will focus on the features of this example.

本例の自動調心ころ軸受の場合、案内輪１０の両側面１２ａ、１２ｂのうちの側面１２ａと、この側面１２ａと対向する、上記各球面ころ３の一端面１８ａとの間の環状隙間１３ａに、全周に亙り、スラスト円すいころ軸受１４ａを設けている。又、上記両側面１２ａ、１２ｂのうちの側面１２ｂと、この側面１２ｂと対向する、上記各球面ころ３の一端面１８ｂとの間の環状隙間１３ｂに、全周に亙り、スラスト円すいころ軸受１４ｂを設けている。尚、上記各球面ころ３、３の一端面１８ａ、１８ａの形状は、大きな曲率半径を有する、部分凸球面形状である事が好ましい。
又、上記両スラスト円すいころ軸受１４ａ、１４ｂは、それぞれ、複数の円すいころ１５、１５と、保持器１６ａ、１６ｂとで構成している。これら両円すいころ軸受１４ａ、１４ｂは、軸方向に関して対称な構造である。この為、以下、上記両円すいころ軸受１４ａ、１４ｂのうちの、円すいころ軸受１４ａに関する説明のみを行なう。 In the case of the self-aligning roller bearing of this example, the annular gap 13a between the side surface 12a of the side surfaces 12a, 12b of the guide wheel 10 and the one end surface 18a of each spherical roller 3 facing the side surface 12a. In addition, a thrust tapered roller bearing 14a is provided over the entire circumference. Further, a thrust tapered roller bearing 14b is provided over the entire circumference in an annular gap 13b between the side surface 12b of the both side surfaces 12a and 12b and the one end surface 18b of each spherical roller 3 facing the side surface 12b. Is provided. In addition, it is preferable that the shape of the one end surfaces 18a and 18a of the spherical rollers 3 and 3 is a partially convex spherical shape having a large radius of curvature.
The thrust roller bearings 14a and 14b are composed of a plurality of tapered rollers 15 and 15 and cages 16a and 16b, respectively. These tapered roller bearings 14a and 14b have a symmetrical structure with respect to the axial direction. For this reason, hereinafter, only the tapered roller bearing 14a out of the both tapered roller bearings 14a and 14b will be described.

上記円すいころ軸受１４ａを構成する保持器１６ａは、図３に示す様に、上記各円すいころ１５を、この保持器１６ａに形成したポケット１７内に転動自在に保持している。又、このポケット１７の、軸方向両端に設けた開口縁部のうちの、軸方向一端側（上記球面ころ３の一端面１８ａ側）の開口縁部１９の径方向全部又は一部の円周方向に関する幅Ｈ19を、この開口縁部１９の径方向位置と対応する上記各円すいころ１５の直径Ｄ15よりも小さく（Ｈ19＜Ｄ15）している。この様にして、上記各円すいころ１５が、上記ポケット１７から、上記軸方向一端側に抜け出す事を防止している。
尚、上述した様な、上記各円すいころ１５の抜け出し防止構造は、上記各球面ころ３と上記各円すいころ１５とが相対回転して、これら各円すいころ１５が、これら各球面ころ３の一端面１８ａから円周方向に外れた場合に、これら各円すいころ１５が上記各ポケット１７から上記軸方向一端側に抜け出してしまう事を防止できる構造ならば、上述した構造に限らず、従来から広く知られている抜け出し防止構造を採用する事ができる。 As shown in FIG. 3, the retainer 16a constituting the tapered roller bearing 14a retains each tapered roller 15 in a pocket 17 formed in the retainer 16a so as to be freely rollable. Of the opening edges provided at both ends in the axial direction of the pocket 17, all or a part of the circumference in the radial direction of the opening edge 19 on one end side in the axial direction (on the one end face 18a side of the spherical roller 3). The width H 19 in the direction is smaller than the diameter D 15 of each tapered roller 15 corresponding to the radial position of the opening edge 19 (H 19 <D 15 ). In this way, each of the tapered rollers 15 is prevented from slipping out of the pocket 17 toward the one end side in the axial direction.
Note that, as described above, each of the tapered rollers 15 is prevented from slipping out so that each of the spherical rollers 3 and each of the tapered rollers 15 rotate relative to each other, and each of the tapered rollers 15 is one of the spherical rollers 3. Any structure that can prevent the tapered rollers 15 from slipping out from the pockets 17 toward the one end side in the axial direction when they are separated from the end face 18a in the circumferential direction is not limited to the structure described above, and has been widely used in the past. A known escape prevention structure can be adopted.

この様な、本例の自動調心ころ軸受の場合、上記両スラスト円すいころ軸受１４ａ、１４ｂを設ける事により、従来は滑り接触であった、上記案内輪１０の両側面１２ａ、１２ｂと、これら両側面１２ａ、１２ｂと対向する、各球面ころ３、３の一端面１８ａとの間部分の接触状態を、転がり接触にできる。この為、この間部分で生じる、摩擦を低減する事ができて、この間部分での発熱、摩耗、焼付きを有効に防止する事ができ、自動調心ころ軸受の耐久性を向上する事ができる。   In the case of such a self-aligning roller bearing of this example, by providing both the thrust tapered roller bearings 14a and 14b, both side surfaces 12a and 12b of the guide wheel 10 that have conventionally been in sliding contact, and these The contact state between the opposite end surfaces 18a and 12b and the one end surface 18a of each of the spherical rollers 3 and 3 can be rolling contact. For this reason, it is possible to reduce the friction generated in this portion, effectively prevent heat generation, wear and seizure in this portion, and improve the durability of the self-aligning roller bearing. .

［実施の形態の第２例］
図４〜５は、請求項１、３に対応する、本発明の実施の形態の第２例を示している。
本例の、自動調心ころ軸受の場合、案内輪１０の両側面１２ａ、１２ｂのうちの側面１２ａと、この側面１２ａと対向する、各球面ころ３の一端面１８ａとの間の環状隙間１３ａに全周に亙りスラスト玉軸受２０ａを設けている。又、上記両側面１２ａ、１２ｂのうちの側面１２ｂと、この側面１２ｂと対向する、各球面ころ３の一端面１８ｂとの間の環状隙間１３ｂに全周に亙りスラスト玉軸受２０ｂを設けている。
又、上記両玉軸受２０ａ、２０ｂは、それぞれ、複数の玉２１、２１と、保持器２２ａ、２２ｂとで構成している。
その他の部分の構成及び作用に就いては、上述した実施の形態の第１例と同様であるから、重複する説明は省略する。 [Second Example of Embodiment]
4 to 5 show a second example of an embodiment of the present invention corresponding to claims 1 and 3.
In the case of the self-aligning roller bearing of this example, the annular gap 13a between the side surface 12a of the side surfaces 12a, 12b of the guide wheel 10 and the one end surface 18a of each spherical roller 3 facing the side surface 12a. A thrust ball bearing 20a is provided over the entire circumference. Further, a thrust ball bearing 20b is provided over the entire circumference in an annular gap 13b between the side surface 12b of the both side surfaces 12a and 12b and the one end surface 18b of each spherical roller 3 facing the side surface 12b. .
The ball bearings 20a and 20b are constituted by a plurality of balls 21 and 21 and cages 22a and 22b, respectively.
Since the configuration and operation of the other parts are the same as those in the first example of the above-described embodiment, redundant description is omitted.

本発明は、自動調心ころ軸受の運転時に、軸受内部の摩擦を低減し、発熱、摩耗、焼付きが発生する事を有効に防止すべく、発明したものである。上述した実施の形態の第１〜２例では、前記両環状隙間１３ａ、１３ｂに、前記スラスト円すいころ軸受１４ａ、１４ｂ、又は、前記スラスト玉軸受２０ａ、２０ｂを設けている。但し、上記両環状隙間１３ａ、１３ｂに設ける軸受の構造は、実施の形態の第１〜２例の構造の軸受１４ａ、１４ｂ、２０ａ、２０ｂに限らない。上記両環状隙間１３ａ、１３ｂの形状、及び使用環境等の条件を考慮して、様々な構造の軸受を採用する事ができる。この場合にも、上述した実施の形態の第１〜２例の場合と同様の作用・効果を得る事ができる。   The present invention was invented to reduce friction inside the bearing and effectively prevent the generation of heat, wear and seizure during operation of the self-aligning roller bearing. In the first and second examples of the above-described embodiment, the thrust tapered roller bearings 14a and 14b or the thrust ball bearings 20a and 20b are provided in the annular gaps 13a and 13b. However, the structure of the bearings provided in the annular gaps 13a and 13b is not limited to the bearings 14a, 14b, 20a, and 20b having the structures of the first and second examples of the embodiment. In consideration of conditions such as the shape of the annular gaps 13a and 13b and the usage environment, bearings having various structures can be employed. Also in this case, the same actions and effects as those in the first and second examples of the embodiment described above can be obtained.

本発明の実施の形態の第１例を示す、自動調心ころ軸受の部分断面図。The fragmentary sectional view of the self-aligning roller bearing which shows the 1st example of embodiment of this invention. 同じく、図１のＡ部拡大図。Similarly, the A section enlarged view of FIG. 同じく、図２の拡大Ｂ−Ｂ断面図。Similarly, the expanded BB sectional drawing of FIG. 本発明の実施の形態の第２例を示す、自動調心ころ軸受の部分断面図。The fragmentary sectional view of the self-aligning roller bearing which shows the 2nd example of embodiment of this invention. 同じく、図４のＣ部拡大図。Similarly, the C section enlarged view of FIG. 従来構造の１例を示す、自動調心ころ軸受の部分断面斜視図。The fragmentary sectional perspective view of the self-aligning roller bearing which shows an example of the conventional structure. 同じく、自動調心ころ軸受の部分断面図。Similarly, the fragmentary sectional view of a self-aligning roller bearing.

符号の説明Explanation of symbols

１ 外輪
２ 内輪
３ 球面ころ
４ 保持器
５ 外輪軌道
６ 内輪軌道
７ 主部
８ 内向フランジ部
９ ポケット
１０ 案内輪
１１ 大径側端部
１２ａ、１２ｂ 側面
１３ａ、１３ｂ 環状隙間
１４ａ、１４ｂ スラスト円すいころ軸受
１５ 円すいころ
１６ａ、１６ｂ 保持器
１７ ポケット
１８ａ、１８ｂ 一端面
１９ 開口縁部
２０ａ、２０ｂ スラスト玉軸受
２１ 玉
２２ａ、２２ｂ 保持器 DESCRIPTION OF SYMBOLS 1 Outer ring 2 Inner ring 3 Spherical roller 4 Cage 5 Outer ring raceway 6 Inner ring raceway 7 Main part 8 Inward flange part 9 Pocket 10 Guide ring 11 Large diameter side end part 12a, 12b Side face 13a, 13b Annular clearance 14a, 14b Thrust tapered roller bearing 15 Tapered rollers 16a, 16b Cage 17 Pockets 18a, 18b One end surface 19 Open edge 20a, 20b Thrust ball bearing 21 Balls 22a, 22b Cage

Claims (3)

単一の中心を有する球状凹面である外輪軌道を、その内周面に形成した外輪と、上記外輪軌道と対向する１対の内輪軌道を、その外周面に形成した内輪と、上記外輪軌道と内輪軌道との間に、２列に亙って転動自在に設けられた複数の球面ころと、これら各球面ころを転動自在に保持する複数のポケットを備えた部分円すい筒状の主部を有する１対の保持器と、この保持器の大径側端部の内周面と上記内輪との間で、上記両列のころ同士の列間の環状隙間に設けられた案内輪とを備えた自動調心ころ軸受に於いて、
この案内輪の軸方向両側面と、これら両側面と対向する上記各球面ころの端面との間に、複数の転動体と、これら各転動体を転動自在に保持する保持器とを設けた事を特徴とする自動調心ころ軸受。 An outer ring raceway that is a spherical concave surface having a single center, an outer ring formed on its inner peripheral surface, a pair of inner ring races facing the outer ring raceway, an inner ring formed on its outer peripheral surface, and the outer ring raceway Partially conical cylindrical main portion having a plurality of spherical rollers that can be freely rolled in two rows between the inner ring raceway and a plurality of pockets that can hold these spherical rollers in a freely rolling manner A pair of cages, and a guide wheel provided in an annular gap between the rows of the two rows of rollers between the inner circumferential surface of the large-diameter end of the cage and the inner ring. In the self-aligning roller bearing provided,
A plurality of rolling elements and a cage for holding the rolling elements in a freely rolling manner are provided between both axial side surfaces of the guide wheel and the end surfaces of the spherical rollers facing the both side surfaces. Spherical roller bearings characterized by 各転動体が円すいころである、請求項１に記載した自動調心ころ軸受。   The self-aligning roller bearing according to claim 1, wherein each rolling element is a tapered roller. 各転動体が玉である、請求項１に記載した自動調心ころ軸受。   The self-aligning roller bearing according to claim 1, wherein each rolling element is a ball.
JP2008055658A 2008-03-06 2008-03-06 Self-aligning roller bearing Pending JP2009210078A (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
JP2008055658A JP2009210078A (en) 2008-03-06 2008-03-06 Self-aligning roller bearing

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
JP2008055658A JP2009210078A (en) 2008-03-06 2008-03-06 Self-aligning roller bearing

Publications (1)

Publication Number Publication Date
JP2009210078A true JP2009210078A (en) 2009-09-17

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Country Link
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Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN102494016A (en) * 2011-12-13 2012-06-13 天津市天重江天重工有限公司 Structure improvement for thrust bearing of cylindrical roller
CN106481667A (en) * 2016-12-23 2017-03-08 贵州虹轴轴承有限公司 A kind of Biserial cylindrical roller bearing

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN102494016A (en) * 2011-12-13 2012-06-13 天津市天重江天重工有限公司 Structure improvement for thrust bearing of cylindrical roller
CN106481667A (en) * 2016-12-23 2017-03-08 贵州虹轴轴承有限公司 A kind of Biserial cylindrical roller bearing

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