JP2005069322A - Thrust ball bearing - Google Patents

Thrust ball bearing Download PDF

Info

Publication number
JP2005069322A
JP2005069322A JP2003298789A JP2003298789A JP2005069322A JP 2005069322 A JP2005069322 A JP 2005069322A JP 2003298789 A JP2003298789 A JP 2003298789A JP 2003298789 A JP2003298789 A JP 2003298789A JP 2005069322 A JP2005069322 A JP 2005069322A
Authority
JP
Japan
Prior art keywords
cage
ball
ball bearing
bearing
thrust ball
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Pending
Application number
JP2003298789A
Other languages
Japanese (ja)
Inventor
Masao Yamamoto
雅雄 山本
Akio Fujii
章雄 藤井
Keiichi Murakami
恵一 村上
Kazuhisa Gunji
和久 郡司
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
NSK Ltd
Original Assignee
NSK Ltd
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by NSK Ltd filed Critical NSK Ltd
Priority to JP2003298789A priority Critical patent/JP2005069322A/en
Publication of JP2005069322A publication Critical patent/JP2005069322A/en
Pending legal-status Critical Current

Links

Images

Classifications

    • 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
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/30—Parts of ball or roller bearings
    • F16C33/38—Ball cages
    • F16C33/42—Ball cages made from wire or sheet metal strips
    • F16C33/422—Ball cages made from wire or sheet metal strips made from sheet metal
    • F16C33/425—Ball cages made from wire or sheet metal strips made from sheet metal from a single part, e.g. ribbon cages with one corrugated annular part
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C2240/00—Specified values or numerical ranges of parameters; Relations between them
    • F16C2240/40—Linear dimensions, e.g. length, radius, thickness, gap
    • F16C2240/60—Thickness, e.g. thickness of coatings

Landscapes

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

Abstract

<P>PROBLEM TO BE SOLVED: To provide a thrust ball bearing for increasing load capacity without increase in size of the bearing. <P>SOLUTION: The thrust ball bearing comprises: a first bearing ring 12 having a first raceway surface 11; a second bearing ring 14 having a second raceway surface 13; a plurality of balls 15 disposed to be capable of rolling between the first raceway surface 11 and the second raceway surface 13; and a cage 16 circumferentially holding the plurality of balls 15 at equal intervals. In the cage 16, the board thicknesses of a ball pocket part 17 and around the ball pocket 17 are thicker than the board thickness of a flange part 19 holding the balls. <P>COPYRIGHT: (C)2005,JPO&NCIPI

Description

本発明は、建設機械、農業機械、運搬機械等の産業機械の回転部に使用されるスラスト玉軸受に関する。   The present invention relates to a thrust ball bearing used in a rotating part of an industrial machine such as a construction machine, an agricultural machine, or a transport machine.

従来、スラスト玉軸受は、図５に示されるようなプレス保持器１００を備えている。プレス保持器１００は、板厚が一定の鋼板を曲げプレス加工することで形成されており、玉１１０を保持する玉ポケット部１０１と、玉ポケット部１０１を有する面の径方向両端から軸方向に折り曲げられた玉を抱えるフランジ部１０２とを有する。   Conventionally, a thrust ball bearing is provided with a press cage 100 as shown in FIG. The press cage 100 is formed by bending and pressing a steel plate having a constant plate thickness. The ball pocket portion 101 that holds the ball 110 and the radial direction both ends of the surface having the ball pocket portion 101 are extended in the axial direction. And a flange portion 102 that holds a bent ball.

特に、コンバイン、トラクター、田植え機、芝刈り機等に代表される農業機械では、ギアミッション方式から油圧式無段変速機構（ＨＳＴ：Ｈｙｄｒｏ Ｓｔａｔｉｃ Ｔｒａｎｓｍｉｓｓｉｏｎ）への移行が進んでいる。このような油圧式無段変速機構では、内部にスラスト玉軸受が採用されている（例えば、特許文献１参照。）。
特開２００３−１９４１８３号公報（第３図） In particular, in agricultural machinery represented by a combine, a tractor, a rice planting machine, a lawn mower, and the like, a shift from a gear mission system to a hydraulic continuously variable transmission mechanism (HST) is progressing. In such a hydraulic continuously variable transmission mechanism, a thrust ball bearing is employed inside (see, for example, Patent Document 1).
Japanese Patent Laying-Open No. 2003-194183 (FIG. 3)

近年、油圧式無段変速機はコンパクト化が進んでおり、無段変速機に組み込まれるスラスト玉軸受にもサイズダウンが要求されている。このため、スラスト玉軸受にかかる負荷が相対的に大きくなっており、市場においても軸受の破損（特に保持器破損等）が見られることがある。
また今後、使用機械の大型化に伴う負荷容量の増大や、機械のコンパクト化による軸受サイズの小型化が進むことで、軸受はより過酷な条件下で使用されることになる。 In recent years, hydraulic continuously variable transmissions have been made more compact, and thrust ball bearings incorporated in continuously variable transmissions are also required to be downsized. For this reason, the load applied to the thrust ball bearing is relatively large, and damage to the bearing (particularly breakage of the cage, etc.) may be seen in the market.
Further, in the future, bearings will be used under more severe conditions as the load capacity increases with the increase in the size of the machine used and the size of the bearing becomes smaller due to the compactness of the machine.

また、保持器が磨耗すると、次のような軸受の破損モードが発生することが考えられる。即ち、保持器の磨耗により、保持器のポケット部の磨耗・破損が発生し、破損部分が軸受内部へ侵入する。このため、潤滑不良が起こり、軸受が剥離を引き起こすとことが考えられる。従って、軸受の長寿命化のためには、保持器の強化が必要である。   Further, when the cage is worn, it is considered that the following failure mode of the bearing occurs. That is, due to wear of the cage, the pocket portion of the cage is worn and damaged, and the damaged portion enters the bearing. For this reason, it is considered that poor lubrication occurs and the bearing causes peeling. Therefore, in order to extend the life of the bearing, it is necessary to strengthen the cage.

このため、玉が保持器に大きな力を加えるような使用条件で用いられるスラスト玉軸受においては、保持器全体の肉厚を厚くして保持器の強度をアップすることが考えられる。しかしながら、保持器全体の肉厚を厚くすると、曲げプレス加工が困難になると共に、保持器がスラスト玉軸受の内径側、外径側に飛び出してしまう可能性がある。特に、軸受のキャパシティアップのために玉径を大きくする場合には、軸受のラジアル方向に保持器が飛び出す可能性が高い。   For this reason, in a thrust ball bearing that is used under conditions in which the ball applies a large force to the cage, it is conceivable to increase the strength of the cage by increasing the thickness of the entire cage. However, if the thickness of the entire cage is increased, bending press working becomes difficult, and the cage may jump out to the inner diameter side and outer diameter side of the thrust ball bearing. In particular, when the ball diameter is increased to increase the capacity of the bearing, there is a high possibility that the cage will pop out in the radial direction of the bearing.

本発明は、上記事情に鑑みてなされたもので、その目的は、軸受のサイズをアップせずに負荷容量を増大することができるスラスト玉軸受を提供することである。   The present invention has been made in view of the above circumstances, and an object thereof is to provide a thrust ball bearing capable of increasing a load capacity without increasing the size of the bearing.

本発明の目的は、下記構成により達成される。
（１）第１の軌道面を有する第１の軌道輪と、第２の軌道面を有する第２の軌道輪と、前記第１の軌道面及び前記第２の軌道面間に転動自在に配置された複数の玉と、前記複数の玉を円周方向に亘って等間隔に保持する保持器とを備えたスラスト玉軸受において、
前記保持器は、玉ポケット部及びその近傍部の板厚を、前記玉を抱えるフランジ部の板厚よりも厚くしたことを特徴とするスラスト玉軸受。
（２）前記保持器は、前記フランジ部の板厚を玉径比の０．１０とし、前記玉ポケット部及びその近傍部の板厚を前記玉径比の０．１１〜０．１４としたことを特徴とする（１）に記載のスラスト玉軸受。
（３）前記保持器は、窒化処理が施されていることを特徴とする（１）又は（２）に記載のスラスト玉軸受。 The object of the present invention is achieved by the following configurations.
(1) A first raceway having a first raceway surface, a second raceway having a second raceway surface, and freely rollable between the first raceway surface and the second raceway surface. In a thrust ball bearing comprising a plurality of arranged balls and a cage for holding the plurality of balls at equal intervals over the circumferential direction,
The retainer is a thrust ball bearing characterized in that the ball pocket portion and the vicinity thereof are thicker than the flange portion holding the ball.
(2) In the cage, the thickness of the flange portion is set to 0.10 of the ball diameter ratio, and the thickness of the ball pocket portion and the vicinity thereof is set to 0.11 to 0.14 of the ball diameter ratio. The thrust ball bearing according to (1), characterized in that:
(3) The thrust ball bearing according to (1) or (2), wherein the cage is nitrided.

本発明によれば、保持器の玉ポケット部及びその近傍部の板厚を、玉を抱えるフランジ部の板厚よりも厚くしたので、保持器強度、耐磨耗性をアップしてスラスト玉軸受の耐久性を向上させることができる。
特に、フランジ部の板厚を玉径比の０．１０とし、玉ポケット部及びその近傍部の板厚を前記玉径比の０．１１〜０．１４としたので、玉ポケット部の磨耗が起点と考えられる軸受の破損モードに対して玉ポケット部が強化され、一方、プレス加工による曲げ性を考慮しフランジ部の板厚を玉ポケット部より薄くしている。なお、玉ポケット部の板厚の上限を玉径比の０．１４としたのは、保持器の加工性や経済性を考慮したものである。 According to the present invention, since the thickness of the ball pocket portion of the cage and the vicinity thereof is made thicker than the thickness of the flange portion holding the ball, the strength of the cage and the wear resistance are increased, and the thrust ball bearing The durability of can be improved.
Particularly, since the thickness of the flange portion is 0.10 of the ball diameter ratio, and the thickness of the ball pocket portion and the vicinity thereof is 0.11 to 0.14 of the ball diameter ratio, the wear of the ball pocket portion is reduced. The ball pocket is strengthened against the failure mode of the bearing, which is considered to be the starting point, while the thickness of the flange is made thinner than the ball pocket in consideration of bendability by press working. The upper limit of the thickness of the ball pocket portion is set to a ball diameter ratio of 0.14 in consideration of the workability and economical efficiency of the cage.

また、保持器に窒化処理（タフトライド処理）を施したことで、保持器の強度、耐磨耗性をさらに向上することができる。
なお、フランジ部の板厚を玉径比の０．１０としたが、実際にばらつきを考慮すると、フランジ部の板厚は、玉径比の０．０７〜０．１３の範囲となる。 Moreover, the strength and wear resistance of the cage can be further improved by performing nitriding treatment (tuftride treatment) on the cage.
In addition, although the plate | board thickness of the flange part was set to 0.10 of the ball diameter ratio, when variation is actually considered, the plate | board thickness of a flange part will be the range of 0.07-0.13 of a ball diameter ratio.

以下、図面を参照して、本発明の一実施形態に係るスラスト玉軸受について詳細に説明する。
図１に示されるように、スラスト玉軸受１０は、第１の軌道面１１を有する第１の軌道輪１２と、第２の軌道面１３を有する第２の軌道輪１４と、第１の軌道面１１と第２の軌道面１３との間に転動自在に配置された複数の玉１５とを備える。さらに、スラスト玉軸受１０は、複数の玉１５を円周方向に亘って等間隔に保持する保持器１６を備える。 Hereinafter, a thrust ball bearing according to an embodiment of the present invention will be described in detail with reference to the drawings.
As shown in FIG. 1, the thrust ball bearing 10 includes a first race ring 12 having a first raceway surface 11, a second race ring 14 having a second raceway surface 13, and a first raceway. A plurality of balls 15 are provided between the surface 11 and the second raceway surface 13 so as to be freely rollable. Further, the thrust ball bearing 10 includes a cage 16 that holds the plurality of balls 15 at equal intervals over the circumferential direction.

保持器１６は、図２（ａ）に示されるように、軸方向に貫通して玉１５を保持する玉ポケット部１７とその近傍部を構成する保持部１８と、玉ポケット部１７を有する保持部１８の径方向両端から軸方向に折り曲げられたフランジ部１９とを有する。保持器１６は、玉１５が保持器１６から脱落せず、且つ、玉１５がスムーズに回転できるように形成されており、フランジ部１９は、図３に示されるように、円周方向に隣接する玉１５間において間隔を狭め、玉１５を抱えるように形成されている。   As shown in FIG. 2A, the cage 16 has a ball pocket portion 17 that penetrates in the axial direction and holds the ball 15, a holding portion 18 that constitutes the vicinity thereof, and a ball pocket portion 17. The flange portion 19 is bent in the axial direction from both radial ends of the portion 18. The cage 16 is formed so that the balls 15 do not fall off the cage 16 and the balls 15 can rotate smoothly, and the flange portion 19 is adjacent in the circumferential direction as shown in FIG. The interval between the balls 15 is narrowed so that the balls 15 are held.

保持器１６は、図２（ｂ）に示されるように、玉ポケット部１７が打抜かれた環状の保持器部材２０の内周部２１と外周部２２を曲げプレス加工することでフランジ部１９を構成している。玉ポケット部１７及びその近傍部を構成する保持部１８の板厚は、フランジ部１９を構成する内周部２１と外周部２２の板厚より厚く構成されており、具体的には、玉径をＤａとすると、フランジ部１９を構成する内周部２１と外周部２２の厚さは０．１０Ｄａであり、玉ポケット部１７及びその近傍部を構成する保持部１８の厚さは０．１１Ｄａ〜０．１４Ｄａに設定されている。   As shown in FIG. 2B, the cage 16 is formed by bending and pressing the inner peripheral portion 21 and the outer peripheral portion 22 of the annular retainer member 20 from which the ball pocket portion 17 is punched. It is composed. The thickness of the ball pocket portion 17 and the holding portion 18 constituting the vicinity thereof is configured to be thicker than the thickness of the inner peripheral portion 21 and the outer peripheral portion 22 constituting the flange portion 19. Is Da, the thickness of the inner peripheral portion 21 and the outer peripheral portion 22 constituting the flange portion 19 is 0.10 Da, and the thickness of the ball pocket portion 17 and the holding portion 18 constituting the vicinity thereof is 0.11 Da. It is set to .about.0.14 Da.

なお、保持部１８の周方向長さＬは、玉ポケット部１７の最大径より若干大きく設定されている。また、保持部１８と内周部２１及び外周部２２とのつなぎ部分は、成形後に亀裂等が生じないように丸面取りが施されている。   The circumferential length L of the holding portion 18 is set slightly larger than the maximum diameter of the ball pocket portion 17. In addition, the connecting portion between the holding portion 18 and the inner peripheral portion 21 and the outer peripheral portion 22 is chamfered so that cracks and the like do not occur after molding.

また、保持器１６を構成する保持器部材２０は、窒化処理であるタフトライド処理が施されている。タフトライド処理は、保持器部材２０を５７０±１０℃の塩浴に２５±５分間浸漬することで、保持器部材の表面に窒化層を形成している。これにより、保持器１６は、Ｈｍｖ３００〜４００の表面硬さ、Ｈｖ１００以上の芯部硬さを得ることができる。   In addition, the cage member 20 constituting the cage 16 is subjected to a tuftride process which is a nitriding process. In the tuftride treatment, the nitride member is formed on the surface of the cage member by immersing the cage member 20 in a salt bath at 570 ± 10 ° C. for 25 ± 5 minutes. Thereby, the holder | retainer 16 can obtain the surface hardness of Hmv300-400, and the core part hardness of Hv100 or more.

次に、ポケット部及びその近傍部の板厚が異なる本実施形態の保持器Ａ，Ｂと従来の保持器Ｃを用いて、表１に示されるような保持器の強度比較を計算によって行った。なお、保持器Ａ〜Ｃのその他の形状は同一のものとし、フランジ部の板厚は、いずれも玉径比の０．１０とする。   Next, using the cages A and B of the present embodiment and the conventional cage C having different thicknesses in the pocket portion and the vicinity thereof, the strength comparison of the cages as shown in Table 1 was performed by calculation. . The other shapes of the cages A to C are the same, and the plate thickness of the flange portion is 0.10, which is the ball diameter ratio.

Figure 2005069322
Figure 2005069322

表１から明らかなように、従来の保持器Ｃ（ポケット部及びその近傍部の板厚：玉径比の０．１０）と比べ、保持器Ａ（ポケット部及びその近傍部の板厚：玉径比の０．１１）の最大応力は約３／４に、また保持器Ｂ（ポケット部及びその近傍部の板厚：玉径比の０．１４）の最大応力は約１／２に緩和されている。従って、ポケット部及びその近傍部の板厚を厚くすることで、保持器の強度が向上することが確認された。   As is apparent from Table 1, compared to the conventional cage C (thickness of the pocket portion and its vicinity: ball diameter ratio of 0.10), the cage A (thickness of the pocket and its vicinity: ball) The maximum stress of the diameter ratio of 0.11) is reduced to about 3/4, and the maximum stress of the cage B (thickness of the pocket and its vicinity: 0.14 of the ball diameter ratio) is relaxed to about 1/2. Has been. Therefore, it was confirmed that the strength of the cage is improved by increasing the thickness of the pocket portion and the vicinity thereof.

次に、タフトライド処理を施した保持器と、ＳＰＣＣ材からなる同一形状の保持器とを用いて、強度及び磨耗特性比較を実験によって行った。
その結果、ＳＰＣＣ材に対してタフトライド処理した材料の引っ張り強度は、約１．７倍となった。また、ＳＰＣＣ材に対してタフトライド処理した材料の耐磨耗性は約５倍に増加した。従って、タフトライド処理を施すことで、保持器の強度及び耐磨耗性が向上することが確認された。 Next, the strength and wear characteristics were compared by experiments using a cage having a tuftride treatment and a cage having the same shape made of SPCC material.
As a result, the tensile strength of the tuftride-treated material with respect to the SPCC material was about 1.7 times. In addition, the wear resistance of the material subjected to tuftride treatment with respect to the SPCC material was increased about 5 times. Therefore, it was confirmed that the strength and wear resistance of the cage are improved by performing the tuftride treatment.

図４は、油圧式無段変速機３０にスラスト玉軸受１０が組み込まれた一例を示す。油圧式無段変速機構３０は、図示しないエンジンから入力軸３１に伝達された回転駆動力を油圧力に変換する可変容量ポンプ３２と、油圧力を回転駆動力に戻して出力軸４０に伝達する可変容量モータ４１とを備えており、入力軸３１に伝達された回転駆動力を前進側、後進側の駆動力に無段階に変更して出力軸４０から出力したり、この出力を停止したりする。   FIG. 4 shows an example in which the thrust ball bearing 10 is incorporated in the hydraulic continuously variable transmission 30. The hydraulic continuously variable transmission mechanism 30 includes a variable displacement pump 32 that converts a rotational driving force transmitted from an engine (not shown) to an input shaft 31 into an oil pressure, and returns the oil pressure to the rotational driving force and transmits the hydraulic pressure to the output shaft 40. And a variable displacement motor 41. The rotational driving force transmitted to the input shaft 31 is steplessly changed to the driving force on the forward side and the reverse side and output from the output shaft 40, or the output is stopped. To do.

可変容量ポンプ３２は、入力軸３１と一体回動するシリンダブロック３３と、シリンダブロック３３の周方向複数箇所に配置され、ピストン室３４内を往復動するノーズピストン３５と、ガイドブロック３６のガイド面に沿って回動する斜板３７とを備えている。可変容量ポンプ３２は、斜板３７が回動操作することで、ノーズピストン３５の往復動ストロークを変化し、ピストン室３４が吐出する油量を変化している。斜板３７には、スラスト玉軸受１０がノーズピストン３５の先端部と接触する位置に配置されており、スラスト軸受１０は斜板３７と共に回動する。   The variable displacement pump 32 includes a cylinder block 33 that rotates integrally with the input shaft 31, a nose piston 35 that is reciprocated in the piston chamber 34, and a guide surface of the guide block 36. And a swash plate 37 rotating along the axis. The variable displacement pump 32 rotates the swash plate 37 to change the reciprocating stroke of the nose piston 35 and change the amount of oil discharged from the piston chamber 34. On the swash plate 37, the thrust ball bearing 10 is disposed at a position in contact with the tip of the nose piston 35, and the thrust bearing 10 rotates together with the swash plate 37.

なお、上述した油圧式無段変速機３０は以下の条件で使用されるもので、本発明のスラスト玉軸受１０はこのような環境下でも十分な耐久性を備えたものとなる。   The above-described hydraulic continuously variable transmission 30 is used under the following conditions, and the thrust ball bearing 10 of the present invention has sufficient durability even in such an environment.

＜油圧式無段変速機の使用例＞
回転速度：２７００ｍｍ−１（最高）
ラジアル荷重：１３１０Ｎ（最大）
アキシアル荷重：７３４０Ｎ（最大）
温度：１１０℃
潤滑方式：オイル潤滑 <Usage example of hydraulic continuously variable transmission>
Rotational speed: 2700mm -1 (maximum)
Radial load: 1310N (maximum)
Axial load: 7340N (maximum)
Temperature: 110 ° C
Lubrication method: Oil lubrication

従って、本実施形態によれば、保持器１６の玉ポケット部１７及びその近傍部の板厚を、玉を抱えるフランジ部１９の板厚よりも厚くしたので、保持器強度、耐磨耗性をアップしてスラスト玉軸受１０の耐久性を向上させることができる。
特に、フランジ部１９の板厚を玉径比の０．１０とし、玉ポケット部１７及びその近傍部の板厚を前記玉径比の０．１１〜０．１４としたので、玉ポケット部１７の磨耗が起点と考えられる軸受の破損モードに対して玉ポケット部１７が強化されており、一方、プレス加工による曲げ性を考慮してフランジ部１９の板厚を玉ポケット部１７より薄くしている。なお、玉ポケット部１７の板厚の上限を玉径比の０．１４としたのは、保持器１６の加工性や経済性を考慮したものである。 Therefore, according to this embodiment, since the thickness of the ball pocket portion 17 of the cage 16 and the vicinity thereof is made thicker than the thickness of the flange portion 19 holding the ball, the cage strength and wear resistance are improved. The durability of the thrust ball bearing 10 can be improved.
Particularly, since the plate thickness of the flange portion 19 is set to 0.10 of the ball diameter ratio, and the plate thickness of the ball pocket portion 17 and the vicinity thereof is set to 0.11 to 0.14 of the ball diameter ratio, the ball pocket portion 17 The ball pocket portion 17 is strengthened against the failure mode of the bearing, which is considered to be the starting point of wear, while the thickness of the flange portion 19 is made thinner than the ball pocket portion 17 in consideration of bendability by press working. Yes. The upper limit of the thickness of the ball pocket portion 17 is set to a ball diameter ratio of 0.14 in consideration of the workability and economical efficiency of the cage 16.

また、保持器１６に窒化処理（タフトライド処理）を施したことで、保持器１６の強度、耐磨耗性をさらに向上することができる。
なお、フランジ部１９の板厚を玉径比の０．１０としたが、実際にばらつきを考慮すると、フランジ部１９の板厚は、玉径比の０．０７〜０．１３の範囲となる。 Moreover, the strength and wear resistance of the cage 16 can be further improved by performing nitriding treatment (tuftride treatment) on the cage 16.
In addition, although the plate | board thickness of the flange part 19 was set to 0.10 of the ball diameter ratio, if variation is actually considered, the plate | board thickness of the flange part 19 will be the range of 0.07-0.13 of a ball diameter ratio. .

また、本発明は、以上に説明した各実施の形態に限定されるものではなく、適宜な変形、改良等が可能である。
本実施形態では、スラスト玉軸受が油圧式無段変速機に組み込まれた例を示したが、本発明のスラスト玉軸受は、油圧式無段変速機に限らず各種装置に適用可能である。 Further, the present invention is not limited to the embodiments described above, and appropriate modifications and improvements can be made.
In the present embodiment, an example in which a thrust ball bearing is incorporated in a hydraulic continuously variable transmission has been described. However, the thrust ball bearing of the present invention is not limited to a hydraulic continuously variable transmission and can be applied to various devices.

本発明に係るスラスト玉軸受を示す断面図である。It is sectional drawing which shows the thrust ball bearing which concerns on this invention. 図１にスラスト玉軸受の保持器を示し、（ａ）は、成形後の保持器の断面図であり、成形前の保持器本体の断面図である。FIG. 1 shows a cage for a thrust ball bearing, wherein (a) is a cross-sectional view of the cage after molding, and is a cross-sectional view of the cage body before molding. 玉が保持された保持器の形状を示す側面図である。It is a side view which shows the shape of the holder | retainer with which the ball | bowl was hold | maintained. 本発明に係るスラスト玉軸受が組み込まれた油圧式無段変速機の例を示す断面図である。It is sectional drawing which shows the example of the hydraulic continuously variable transmission in which the thrust ball bearing which concerns on this invention was integrated. 従来のスラスト玉軸受の保持器を示す断面図である。It is sectional drawing which shows the holder | retainer of the conventional thrust ball bearing.

符号の説明Explanation of symbols

１０ スラスト玉軸受
１２ 第１の軌道輪
１４ 第２の軌道輪
１５ 玉
１６ 保持器
１７ 玉ポケット部
１９ フランジ部
２１ ケース本体
３０ 油圧式無段変速機 DESCRIPTION OF SYMBOLS 10 Thrust ball bearing 12 1st track ring 14 2nd track ring 15 Ball 16 Cage 17 Ball pocket part 19 Flange part 21 Case main body 30 Hydraulic continuously variable transmission

Claims (3)

第１の軌道面を有する第１の軌道輪と、第２の軌道面を有する第２の軌道輪と、前記第１の軌道面及び前記第２の軌道面間に転動自在に配置された複数の玉と、前記複数の玉を円周方向に亘って等間隔に保持する保持器とを備えたスラスト玉軸受において、
前記保持器は、玉ポケット部及びその近傍部の板厚を、前記玉を抱えるフランジ部の板厚よりも厚くしたことを特徴とするスラスト玉軸受。 The first raceway having the first raceway surface, the second raceway having the second raceway surface, and the first raceway surface and the second raceway surface are rotatably arranged. In a thrust ball bearing comprising a plurality of balls and a cage for holding the plurality of balls at equal intervals over the circumferential direction,
The retainer is a thrust ball bearing characterized in that the ball pocket portion and the vicinity thereof are thicker than the flange portion holding the ball. 前記保持器は、前記フランジ部の板厚を玉径比の０．１０とし、前記玉ポケット部及びその近傍部の板厚を前記玉径比の０．１１〜０．１４としたことを特徴とする請求項１に記載のスラスト玉軸受。   The cage is characterized in that a plate thickness of the flange portion is set to a ball diameter ratio of 0.10, and a plate thickness of the ball pocket portion and the vicinity thereof is set to a ball diameter ratio of 0.11 to 0.14. The thrust ball bearing according to claim 1. 前記保持器は、窒化処理が施されていることを特徴とする請求項１又は２に記載のスラスト玉軸受。   The thrust ball bearing according to claim 1, wherein the cage is subjected to nitriding treatment.
JP2003298789A 2003-08-22 2003-08-22 Thrust ball bearing Pending JP2005069322A (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
JP2003298789A JP2005069322A (en) 2003-08-22 2003-08-22 Thrust ball bearing

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
JP2003298789A JP2005069322A (en) 2003-08-22 2003-08-22 Thrust ball bearing

Publications (1)

Publication Number Publication Date
JP2005069322A true JP2005069322A (en) 2005-03-17

Family

ID=34404193

Family Applications (1)

Application Number Title Priority Date Filing Date
JP2003298789A Pending JP2005069322A (en) 2003-08-22 2003-08-22 Thrust ball bearing

Country Status (1)

Country Link
JP (1) JP2005069322A (en)

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US8182157B2 (en) * 2005-02-22 2012-05-22 Koyo Bearings Usa Llc Thrust bearing assembly
US20120170885A1 (en) * 2009-09-18 2012-07-05 Schaeffler Technologies AG & Co. KG Ball roller bearing
JP2012140982A (en) * 2010-12-28 2012-07-26 Nsk Ltd Thrust ball bearing
JP2013064496A (en) * 2011-08-29 2013-04-11 Nsk Ltd Thrust bearing for hydraulic continuously variable transmission
DE102012208790A1 (en) * 2012-05-25 2013-11-28 Schaeffler Technologies AG & Co. KG Roller body guide cage for guiding balls in axial ball bearing, has annular disk body provided with sliding piece structure that forms sliding contact surface, where body is axially supported at ball race by sliding contact surface

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US8182157B2 (en) * 2005-02-22 2012-05-22 Koyo Bearings Usa Llc Thrust bearing assembly
US20120170885A1 (en) * 2009-09-18 2012-07-05 Schaeffler Technologies AG & Co. KG Ball roller bearing
US8596873B2 (en) * 2009-09-18 2013-12-03 Schaeffler Technologies AG & Co. KG Ball roller bearing
JP2012140982A (en) * 2010-12-28 2012-07-26 Nsk Ltd Thrust ball bearing
JP2013064496A (en) * 2011-08-29 2013-04-11 Nsk Ltd Thrust bearing for hydraulic continuously variable transmission
DE102012208790A1 (en) * 2012-05-25 2013-11-28 Schaeffler Technologies AG & Co. KG Roller body guide cage for guiding balls in axial ball bearing, has annular disk body provided with sliding piece structure that forms sliding contact surface, where body is axially supported at ball race by sliding contact surface

Similar Documents

Publication Publication Date Title
US7685717B2 (en) Method for manufacturing a bearing raceway member
CN100400907C (en) Rotation support device for compressor pulley
US8210754B2 (en) Radial roller bearing having hollow rollers
KR100382448B1 (en) Method of fabricating pin retaining ring for internal gear, internal meshing planetary gear structure, and hydraulic motor pump
KR20160062077A (en) Retainer for needle roller bearing, and needle roller bearing
JPWO2015076271A1 (en) Cylindrical roller bearing and transmission bearing device
JP2005069322A (en) Thrust ball bearing
JP6036008B2 (en) Thrust bearing for hydraulic continuously variable transmission
JP2008032052A (en) Thrust roller bearing
JP2013047557A (en) Thrust bearing
JP2003166624A (en) Support structure for rotary shaft
JP2008095898A (en) One-way clutch and one-way clutch built-in type rotation transmission device
JP2006342904A (en) Pinion shaft and planetary gear device
EP1416177A2 (en) Bearing and method of assembling the bearing
JP2008215566A (en) Thrust bearing for hydraulic continuously variable transmission
JP2006258262A (en) Double-row rolling bearing
JP2005016710A (en) Needle bearing
CN211525484U (en) Automobile transmission shaft with novel shaft retainer ring
JP2006349111A (en) One way clutch and pulley with built-in clutch using the same
JP5267086B2 (en) Shell-type full needle bearing with seal ring and manufacturing method thereof
JP2010196809A (en) Shell type needle bearing with seal ring
WO2016190026A1 (en) Thrust bearing for hydraulic continuously variable transmission
JP2024087348A (en) Thrust ball bearing
JP5561896B2 (en) Needle roller bearing and crankshaft support structure
JP2024087352A (en) Thrust ball bearing

Legal Events

Date Code Title Description
RD04 Notification of resignation of power of attorney

Free format text: JAPANESE INTERMEDIATE CODE: A7424

Effective date: 20060325