JP2007192252A - Thrust roller bearing - Google Patents

Thrust roller bearing Download PDF

Info

Publication number
JP2007192252A
JP2007192252A JP2006008709A JP2006008709A JP2007192252A JP 2007192252 A JP2007192252 A JP 2007192252A JP 2006008709 A JP2006008709 A JP 2006008709A JP 2006008709 A JP2006008709 A JP 2006008709A JP 2007192252 A JP2007192252 A JP 2007192252A
Authority
JP
Japan
Prior art keywords
cage
roller
pocket
roller bearing
radial direction
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
JP2006008709A
Other languages
Japanese (ja)
Inventor
Katsuhiko Chihara
勝彦 千原
Masaki Toyama
正基 外山
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.)
JTEKT Corp
Original Assignee
JTEKT Corp
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 JTEKT Corp filed Critical JTEKT Corp
Priority to JP2006008709A priority Critical patent/JP2007192252A/en
Publication of JP2007192252A publication Critical patent/JP2007192252A/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
    • F16C19/22—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
    • 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
    • F16C33/467—Details of individual pockets, e.g. shape or roller retaining means
    • 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
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D7/00—Slip couplings, e.g. slipping on overload, for absorbing shock
    • F16D7/007—Slip couplings, e.g. slipping on overload, for absorbing shock the torque being transmitted and limited by rolling surfaces skidding, e.g. skew needle 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
    • F16C2240/00—Specified values or numerical ranges of parameters; Relations between them
    • F16C2240/30—Angles, e.g. inclinations

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 roller bearing capable of preventing increase in the amount of sliding of a roller and a bearing ring when rotating relatively and preventing fretting wear and peeling-off of a raceway track and the roller at load synchronous rotation time or non-rotation time. <P>SOLUTION: A cage pocket 2 provided in a cage 1 of the thrust roller bearing has a parallelogram shape, a side 21 on an outer peripheral side and a side 23 on an inner peripheral side are perpendicular to the radial direction (O-R) of the cage 1, and a side 24 on one side and a side 22 on the other side in substantially circumferential direction are inclined in the radial direction by only a predetermined angle θ. Consequently, an end face 31 on an outer peripheral side of the roller 3 is abutted on the side 21 on the outer peripheral side of the cage pocket 2 and rotates smoothly at relative rotation time. On the other hand, a side face 34 of the roller 3 is abutted on the side 24 on one side of the cage pocket 2 at load synchronous rotation time or non-rotation time. That is, when the bearing ring performs vibration movement, the cage 1 and the roller 3 are integrated to promote relative rotation for the bearing ring. <P>COPYRIGHT: (C)2007,JPO&INPIT

Description

本発明は、スラストころ軸受（スラストニードル軸受を含む）、特に、軌道やころにフレティング摩耗や剥離が生じないようにしたスラストころ軸受に関する。   The present invention relates to a thrust roller bearing (including a thrust needle bearing), and more particularly to a thrust roller bearing that prevents fretting wear and separation from occurring on raceways and rollers.

スラストころ軸受は、たとえば、自動車のトランスミッション等の回転部分に装着され、回転軸に作用するスラスト荷重（軸方向の荷重）を支承するものであって、一対の円環状の環状板（以下「軌道輪」と称す）と、一対の軌道輪の間に配置される保持器と、保持器に設けられた保持器ポケットに収納される複数のころと、を具備している。そして、一対の軌道輪が相対的に回転（双方が相違する回転数で回転、または一方のみが回転）とき、ころは自転しながら公転する。   A thrust roller bearing is mounted on a rotating part of an automobile transmission or the like, for example, and supports a thrust load (axial load) acting on a rotating shaft, and a pair of annular annular plates (hereinafter referred to as “tracks”). And a cage disposed between the pair of race rings, and a plurality of rollers accommodated in a cage pocket provided in the cage. When the pair of races rotate relatively (both rotate at different rotational speeds or only one rotates), the rollers revolve while rotating.

ところが、自動車のＡＴ（自動変速機）では、速度段によってはスラストころ軸受に荷重がかかっていながら一対の軌道輪が相対的に回転しない状態（以下「負荷同期回転時」と称す）、あるいは一対の軌道輪の双方が回転停止した状態（以下「無回転時」と称す）で用いられる場合がある。
また、近年、自動車の燃費向上のために、ＡＴの前段であるトルクコンバータがロックアップ状態で使用される場合が多くなっている。このとき、ロックアップ状態で負荷同期回転時になると、エンジンからの振動によりスラストころ軸受の軌道やころにフレティング摩耗や剥離が生じるようになった。 However, in an AT (automatic transmission) of an automobile, depending on the speed stage, a load is applied to the thrust roller bearing, but the pair of race rings do not rotate relatively (hereinafter referred to as “load synchronous rotation”), or a pair May be used in a state where both of the race rings stop rotating (hereinafter referred to as “no rotation”).
In recent years, in order to improve the fuel efficiency of automobiles, torque converters, which are the front stage of ATs, are often used in a locked-up state. At this time, when load-synchronized rotation occurs in the locked-up state, fretting wear or separation occurs on the raceway or roller of the thrust roller bearing due to vibration from the engine.

そこで、このようなフレティング摩耗等の発生を防止する目的で、保持器ポケットの軸線を保持器の半径と角度をなすようにした発明が開示されている。
すなわち、保持器ポケットところとの半径方向のクリアランスに着目して、軸受レース（軌道輪に同じ）が振動運動するとき、時計回りの相対微小回転によってころに作用するモーメントと、反時計回りの相対微小回転によってころに作用するモーメントとの差から、ころが半径に対して一方向に回動しようとすることに鑑み、矩形の保持器ポケットを半径方向に対してスピンの方向とは反対の方向に傾けていた。そして、これによって保持器を一方向に余分に回転させようとしていた（例えば、特許文献１参照）。 Therefore, an invention is disclosed in which the axis of the cage pocket is angled with the radius of the cage for the purpose of preventing the occurrence of such fretting wear.
In other words, paying attention to the radial clearance from the cage pocket, when the bearing race (same as the race) oscillates, the moment acting on the rollers due to the clockwise relative minute rotation and the counterclockwise relative In consideration of the fact that the roller tries to rotate in one direction with respect to the radius due to the difference from the moment acting on the roller due to the minute rotation, the rectangular cage pocket is in the direction opposite to the spin direction with respect to the radial direction. Tilt to. And it was going to rotate the retainer extra one way by this (for example, refer to patent documents 1).

また、一対の軌道輪が相対的に回転する際（以下「相対回転時」と称す）、ころの長手方向の端部が保持器ポケットに局部的に当接（いわゆる片当たりに同じ）しないでスピンするよう、保持器ポケットの長手方向の辺を保持器の半径方向に一致させる発明が開示されている。すなわち、保持器ポケットが内周側に上辺を、外周側に下辺を、保持器の中心に向う方向に斜辺を、有する台形にしていた（例えば、特許文献２参照）。   Further, when the pair of race rings relatively rotate (hereinafter referred to as “relative rotation”), the end portions in the longitudinal direction of the rollers do not locally contact the so-called cage pocket (so-called same per contact). An invention is disclosed in which the longitudinal sides of the cage pocket coincide with the radial direction of the cage for spinning. That is, the cage pocket has a trapezoidal shape having an upper side on the inner circumferential side, a lower side on the outer circumferential side, and a hypotenuse in a direction toward the center of the cage (for example, see Patent Document 2).

特公昭３８−１１５７号公報（第１頁、第１図）Japanese Examined Patent Publication No. 38-1157 (first page, Fig. 1) 米国特許第４０７７６８３号公報（第２頁、第１図）US Pat. No. 4,077,683 (page 2, FIG. 1)

しかしながら、前記特許文献１に開示された発明は、複数の保持器ポケットのうち２つ以上の保持器ポケットについてのみ、その軸線を半径に対して傾けただけであるため、数量が少ない場合には、かかる傾けた効果が期待できないという問題があった。一方、全てのころを傾けたのでは、相対回転時にころと軌道輪とのすべり量が増大するという問題があった。
また、前記特許文献２に開示された発明は、相対回転時に保持器ポケットの斜辺の全長にころの長手方向の全長が当接するものの、負荷同期回転時あるいは無回転時においては、軌道やころのフレティング摩耗や剥離を防止することができないという問題があった。 However, in the invention disclosed in Patent Document 1, only the two or more cage pockets among the plurality of cage pockets are merely tilted with respect to the radius. There was a problem that such a tilted effect could not be expected. On the other hand, if all the rollers are tilted, there is a problem that the amount of sliding between the rollers and the raceway increases during relative rotation.
In the invention disclosed in Patent Document 2, the total length of the roller in the longitudinal direction abuts the entire length of the hypotenuse of the cage pocket at the time of relative rotation, but at the time of load synchronous rotation or non-rotation, There was a problem that fretting wear and peeling could not be prevented.

本発明は、このような問題を解決するためになされたものであり、相対回転時にころと軌道輪とのすべり量の増大を防止すると共に、負荷同期回転時あるいは無回転時における軌道やころのフレティング摩耗や剥離を防止する、スラストころ軸受を提供することを目的とする。   The present invention has been made to solve such a problem, and prevents an increase in the amount of slip between the roller and the raceway during relative rotation, and also prevents the raceway and roller during load synchronous rotation or non-rotation. An object of the present invention is to provide a thrust roller bearing that prevents fretting wear and peeling.

（１）本発明のスラストころ軸受は、一対の環状板と、該環状板の間に配置される円環状の保持器と、該保持器に設けられた保持器ポケットに収容されるころと、を有するスラストころ軸受であって、
前記保持器ポケットの外周側の辺が前記保持器の半径方向に対して垂直であり、かつ前記保持器ポケットの略円周方向の一方の辺が前記保持器の半径方向に対して所定の角度傾斜していることを特徴とする。 (1) A thrust roller bearing of the present invention has a pair of annular plates, an annular retainer disposed between the annular plates, and a roller accommodated in a retainer pocket provided in the retainer. A thrust roller bearing,
The outer peripheral side of the cage pocket is perpendicular to the radial direction of the cage, and one side in the substantially circumferential direction of the cage pocket is at a predetermined angle with respect to the radial direction of the cage It is characterized by being inclined.

（２）また、前記保持器ポケットが平行四辺形であることを特徴とする。   (2) Further, the cage pocket is a parallelogram.

（３）さらに、前記ころが、前記保持器の半径方向から前記保持器の半径方向に対して前記所定の角度傾斜した方向の範囲を回動自在であることを特徴とする。   (3) Further, the roller is rotatable in a range in a direction inclined by the predetermined angle with respect to a radial direction of the cage from a radial direction of the cage.

したがって、本発明のスラストころ軸受は以下のような効果を奏す。
（ｉ）保持器ポケットの外周側の辺が保持器の半径方向に対して垂直であるため、相対回転時に、かかる外周側の辺にころの端部が案内されるから、ころは滑らかに回転する。
（ｉｉ）同時に、保持器ポケットの略円周方向の一方の辺が保持器の半径方向に対して所定の角度傾斜しているため、負荷同期回転時あるいは無回転時に作用する振動（ころに作用するモーメントとの差に同じ）によって、ころの回動（スピンの方向とは反対方向に回動する）が可能になるから、ころと保持器とが一体的に軌道輪に対して相対的に移動する。よって、局部的な軌道やころのフレティング摩耗や剥離が防止される。 Therefore, the thrust roller bearing of the present invention has the following effects.
(I) Since the outer peripheral side of the cage pocket is perpendicular to the radial direction of the cage, the rollers rotate smoothly because the end of the roller is guided to the outer peripheral side during relative rotation. To do.
(Ii) At the same time, since one side in the substantially circumferential direction of the cage pocket is inclined at a predetermined angle with respect to the radial direction of the cage, vibration acting on the load synchronous rotation or non-rotation (acting on the rollers) The same as the difference between the moment and the roller), the roller can rotate (rotate in the direction opposite to the spin direction). Moving. Therefore, local tracks and fretting wear and peeling of the rollers are prevented.

図１および図２は本発明の実施形態に係るスラストころ軸受の保持器を模式的に示す、図１は部分平面図、図２は部分拡大図である。図１および図２において、図示しないスラストころ軸受は、図示しない一対の環状板と、該環状板の間に配置される円環状の保持器１と、保持器１に設けられた保持器ポケット２に収容されるころ３と、を有している。なお、保持器１の外径や内径、保持器ポケット２の数量、さらに、ころ３のアスペクト比や面取り等は図示するものに限定するものではない。
保持器ポケット２は平行四辺形であって、外周側の辺２１と内周側の２３とが、保持器１の半径方向（軸心「Ｏ」と位置「Ｒ」とを通る方向に同じ）に対して垂直であり、略円周方向の一方の辺２４と他方の辺２２とが半径方向に対して所定の角度θだけ傾斜している。 1 and 2 schematically show a retainer for a thrust roller bearing according to an embodiment of the present invention. FIG. 1 is a partial plan view, and FIG. 2 is a partially enlarged view. 1 and 2, a thrust roller bearing (not shown) is accommodated in a pair of annular plates (not shown), an annular cage 1 disposed between the annular plates, and a cage pocket 2 provided in the cage 1. And roller 3. The outer diameter and inner diameter of the cage 1, the number of cage pockets 2, and the aspect ratio and chamfering of the rollers 3 are not limited to those illustrated.
The cage pocket 2 is a parallelogram, and the outer side 21 and the inner side 23 are in the radial direction of the cage 1 (the same in the direction passing through the axis “O” and the position “R”). The one side 24 and the other side 22 in the substantially circumferential direction are inclined by a predetermined angle θ with respect to the radial direction.

図２の（ａ）は、相対回転時のころ３の様子を模式的に示している。ころ３の外周側の端面３１は、保持器ポケット２の外周側の辺２１に当接して、回転（自転）している。このとき、ころ３の端面３１の範囲「Ａ−Ｂ」が外周側の辺２１に当接して、軸心「Ｏ」に正対しているから、滑らかの回転する。なお、ころ３の側面３４（たまたま図中、左側のある稜線を示す）の外周側位置「Ｃ」と保持器ポケット２の一方の辺２４とが、また、ころ３の側面３２（たまたま図中、右側のある稜線を示す）の外周側位置「Ｆ」と保持器ポケット２の他方の辺２２とが、それぞれ離れている様子を図示しているが、一方が当接することがある。   (A) of FIG. 2 has shown typically the mode of the roller 3 at the time of relative rotation. The outer peripheral end surface 31 of the roller 3 is in contact with the outer peripheral side 21 of the cage pocket 2 and rotates (autorotates). At this time, the range “A-B” of the end surface 31 of the roller 3 is in contact with the side 21 on the outer peripheral side and directly faces the axis “O”, so that the roller 3 rotates smoothly. It should be noted that the outer peripheral side position “C” of the side surface 34 of the roller 3 (which happens to show a certain ridge line on the left side) and the one side 24 of the cage pocket 2 and the side surface 32 of the roller 3 (which happens to be in the diagram) ), The outer peripheral side position “F” and the other side 22 of the cage pocket 2 are illustrated as being separated from each other, but one of them may come into contact.

図２の（ｂ）は、負荷同期回転時あるいは無回転時のころ３の様子を模式的に示している。ころ３の側面３４が保持器ポケット２の一方の辺２４に当接している。このとき、ころ３の一方の側面３４の範囲「Ｃ−Ｄ」が一方の辺２４に当接しているから、ころ３の回転軸４は半径方向に対して角度θだけ傾斜している。
よって、図示しない軌道輪が振動運動する際に生じるモーメントの作用によって、ころ３の回動が保証されるから、保持器１ところ３とは一体的になって、軌道輪（図示しない）に対する相対回転が促進されることになる。したがって、ころ３は軌道輪（図示しない）に対して相対的に移動するから、軌道やころに局部的に発生するフレティング摩耗や剥離が防止される。 FIG. 2B schematically shows the state of the roller 3 during load synchronous rotation or non-rotation. A side surface 34 of the roller 3 is in contact with one side 24 of the cage pocket 2. At this time, since the range “C-D” of the one side surface 34 of the roller 3 is in contact with the one side 24, the rotation shaft 4 of the roller 3 is inclined by an angle θ with respect to the radial direction.
Therefore, since the rotation of the roller 3 is ensured by the action of the moment generated when the raceway (not shown) oscillates, the cage 1 is integrated with the place 3 and is relative to the raceway (not shown). Rotation will be promoted. Therefore, since the roller 3 moves relative to the race (not shown), fretting wear and separation that occur locally on the race and the roller are prevented.

なお、ころ３の内周側の端面３３の位置「Ｅ」と保持器ポケット２の内周側の辺２３との間に所定の間隔が設けられているが、ころ３がかかる角度θの範囲を回動（逆方向のスピンに相当する）自在である限り、内周側の端面３３の位置「Ｅ」と内周側の辺２３とが、および、外周側の端面３１の位置「Ｂ」と外周側の辺２１とが、それぞれ当接してもよい。また、保持器ポケット２の四隅を直線で図示しているが、ころ３の角度θの範囲の傾動を許容する大きさの隅Ｒを形成してもよい。また、保持器ポケット２が平行四辺形の場合を示しているが、他方の辺２２はころ３の他方の側面３２を案内するものではないから、他方の辺２２はころ３の角度θの範囲の傾動を許容するものであれば、その形状は限定されるものではない。
なお、角度θの大きさは適宜設定されるものであるが、概ね、数度から１５°程度である。 A predetermined interval is provided between the position “E” of the end surface 33 on the inner peripheral side of the roller 3 and the side 23 on the inner peripheral side of the cage pocket 2, but the range of the angle θ over which the roller 3 is applied. Can be rotated (corresponding to spin in the reverse direction) freely, the position “E” of the inner peripheral end surface 33 and the inner peripheral side 23, and the position “B” of the outer peripheral end surface 31. And the outer peripheral side 21 may contact each other. Further, although the four corners of the cage pocket 2 are illustrated by straight lines, corners R having a size that allows tilting in the range of the angle θ of the roller 3 may be formed. Moreover, although the case where the cage pocket 2 is a parallelogram is shown, since the other side 22 does not guide the other side surface 32 of the roller 3, the other side 22 is within the range of the angle θ of the roller 3. The shape is not limited as long as tilting is allowed.
In addition, although the magnitude | size of angle (theta) is set suitably, it is about several degrees to about 15 degrees in general.

本発明は以上の構成であるから、耐久性に優れた各種スラストころ軸受およびスラストニードル軸受として広く利用することができる。   Since this invention is the above structure, it can be widely used as various thrust roller bearings and thrust needle bearings excellent in durability.

本発明の実施形態に係るスラストころ軸受の保持器を示す部分平面図。The fragmentary top view which shows the holder | retainer of the thrust roller bearing which concerns on embodiment of this invention. 本発明の実施形態に係るスラストころ軸受の保持器を示す部分拡大図。The elements on larger scale which show the retainer of the thrust roller bearing which concerns on embodiment of this invention.

符号の説明Explanation of symbols

１ 保持器
２ 保持器ポケット
３ ころ
４ 回転軸
２１ 外周側の辺(保持器ポケット)
２２ 略半径方向の辺(保持器ポケット)
２３ 内周側の辺(保持器ポケット)
２４ 略半径方向の辺(保持器ポケット)
３１ 外周側の端面(ころ)
３２ 側面(ころ)
３３ 外周側の端面(ころ)
３４ 側面(ころ)
θ 傾斜角度
1 Cage 2 Cage Pocket 3 Roller 4 Rotating Shaft 21 Peripheral Side (Cage Pocket)
22 Nearly radial side (retainer pocket)
23 Inner side (retainer pocket)
24 Nearly radial side (retainer pocket)
31 Outer end face (roller)
32 Side (roller)
33 End face (roller) on the outer peripheral side
34 Side (roller)
θ Inclination angle

Claims (3)

一対の環状板と、該環状板の間に配置される円環状の保持器と、該保持器に設けられた保持器ポケットに収容されるころと、を有するスラストころ軸受であって、
前記保持器ポケットの外周側の辺が前記保持器の半径方向に対して垂直であり、かつ前記保持器ポケットの略円周方向の一方の辺が前記保持器の半径方向に対して所定の角度傾斜していることを特徴とするスラストころ軸受。 A thrust roller bearing having a pair of annular plates, an annular retainer disposed between the annular plates, and a roller accommodated in a retainer pocket provided in the retainer,
The outer peripheral side of the cage pocket is perpendicular to the radial direction of the cage, and one side in the substantially circumferential direction of the cage pocket is at a predetermined angle with respect to the radial direction of the cage A thrust roller bearing characterized by being inclined. 前記保持器ポケットが平行四辺形であることを特徴とする請求項１記載のスラストころ軸受。   The thrust roller bearing according to claim 1, wherein the cage pocket is a parallelogram. 前記ころが、前記保持器の半径方向から前記保持器の半径方向に対して前記所定の角度傾斜した方向の範囲を回動自在であることを特徴とする請求項１または２記載のスラストころ軸受。
The thrust roller bearing according to claim 1 or 2, wherein the roller is rotatable in a range in a direction inclined by the predetermined angle with respect to a radial direction of the cage from a radial direction of the cage. .
JP2006008709A 2006-01-17 2006-01-17 Thrust roller bearing Pending JP2007192252A (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
JP2006008709A JP2007192252A (en) 2006-01-17 2006-01-17 Thrust roller bearing

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
JP2006008709A JP2007192252A (en) 2006-01-17 2006-01-17 Thrust roller bearing

Publications (1)

Publication Number Publication Date
JP2007192252A true JP2007192252A (en) 2007-08-02

Family

ID=38448122

Family Applications (1)

Application Number Title Priority Date Filing Date
JP2006008709A Pending JP2007192252A (en) 2006-01-17 2006-01-17 Thrust roller bearing

Country Status (1)

Country Link
JP (1) JP2007192252A (en)

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2009270692A (en) * 2008-05-12 2009-11-19 Ntn Corp Roller with retainer and retainer for roller bearing
JP2015148316A (en) * 2014-02-07 2015-08-20 本田技研工業株式会社 Continuously variable transmission
JP2016161114A (en) * 2015-03-05 2016-09-05 鹿島化学金属株式会社 Thrust bearing and cage thereof
CN106838007A (en) * 2015-10-28 2017-06-13 舍弗勒技术股份两合公司 Thrust bearing, knuckle spindle bearing apparatus and its application
WO2020074030A1 (en) * 2018-10-11 2020-04-16 Schaeffler Technologies AG & Co. KG Chassis for a vehicle

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1494392A (en) * 1922-04-08 1924-05-20 Fred H Van Loozen Antifriction bearing
US4077683A (en) * 1976-03-22 1978-03-07 The Torrington Company Roller thrust bearing cage and roller assembly

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1494392A (en) * 1922-04-08 1924-05-20 Fred H Van Loozen Antifriction bearing
US4077683A (en) * 1976-03-22 1978-03-07 The Torrington Company Roller thrust bearing cage and roller assembly

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2009270692A (en) * 2008-05-12 2009-11-19 Ntn Corp Roller with retainer and retainer for roller bearing
JP2015148316A (en) * 2014-02-07 2015-08-20 本田技研工業株式会社 Continuously variable transmission
JP2016161114A (en) * 2015-03-05 2016-09-05 鹿島化学金属株式会社 Thrust bearing and cage thereof
CN106838007A (en) * 2015-10-28 2017-06-13 舍弗勒技术股份两合公司 Thrust bearing, knuckle spindle bearing apparatus and its application
WO2020074030A1 (en) * 2018-10-11 2020-04-16 Schaeffler Technologies AG & Co. KG Chassis for a vehicle

Similar Documents

Publication Publication Date Title
JP2005069421A (en) Conical roller bearing
JP2008185107A (en) Ball bearing
JP2007192252A (en) Thrust roller bearing
JP2004245251A (en) Automatic centering rolling bearing
JP3114438B2 (en) Rolling bearing
JP2009036348A (en) Tandem type double-row angular contact ball bearing and bearing device for pinion shaft
JP2008133894A (en) Ball bearing retainer
JP2007278406A (en) Roller bearing with cage
JP2003042160A (en) Angular contact ball bearing and main bearing
JP2006214456A (en) Roller bearing
JP2012172763A (en) Thrust roller bearing
JP2018179009A (en) Thrust cylindrical roller bearing
JP2010025191A (en) Self-aligning roller bearing
JP2006258262A (en) Double-row rolling bearing
JP2006183718A (en) Rolling bearing
JP2008064230A (en) Thrust bearing
JP2009210078A (en) Self-aligning roller bearing
JP2004176745A (en) Roller bearing
JP2001082464A (en) Cylindrical roller bearing
JP2009019708A (en) Split type needle roller bearing
JP2007187214A (en) Thrust roller bearing
JP2000274437A (en) Rolling bearing
JP2004239399A (en) Tapered roller bearing
JPH0587132A (en) Roller bearing
JP2006112568A (en) Cylindrical roller bearing

Legal Events

Date Code Title Description
A621 Written request for application examination

Free format text: JAPANESE INTERMEDIATE CODE: A621

Effective date: 20081224

A977 Report on retrieval

Free format text: JAPANESE INTERMEDIATE CODE: A971007

Effective date: 20091124

A131 Notification of reasons for refusal

Free format text: JAPANESE INTERMEDIATE CODE: A131

Effective date: 20100223

A02 Decision of refusal

Free format text: JAPANESE INTERMEDIATE CODE: A02

Effective date: 20100706