JP3039638B2 - Tapered roller bearing - Google Patents
Tapered roller bearingInfo
- Publication number
- JP3039638B2 JP3039638B2 JP10206151A JP20615198A JP3039638B2 JP 3039638 B2 JP3039638 B2 JP 3039638B2 JP 10206151 A JP10206151 A JP 10206151A JP 20615198 A JP20615198 A JP 20615198A JP 3039638 B2 JP3039638 B2 JP 3039638B2
- Authority
- JP
- Japan
- Prior art keywords
- tapered roller
- tapered
- roller bearing
- inner ring
- cage
- 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.)
- Expired - Fee Related
Links
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
- F16C19/34—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
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Rolling Contact Bearings (AREA)
Description
【０００１】[0001]
【発明が属する技術分野】この発明に係る円すいころ軸
受は、自動車のギヤボックスに装着してシャフトを回転
自在に支持したり、或は自動車の懸架装置に装着して、
車軸を回転自在に支持する場合等に利用する。BACKGROUND OF THE INVENTION A tapered roller bearing according to the present invention is mounted on a gear box of an automobile to rotatably support a shaft, or mounted on a suspension system of an automobile.
Used when the axle is rotatably supported.
【０００２】[0002]
【従来の技術】円すい台状の円すいころを組み込んだ円
すいころ軸受は、ラジアル荷重とアキシャル荷重とを支
持する事ができ、しかも耐荷重が大きい為、大きな荷重
が加わる各種回転支持部分に利用されている。この様な
円すいころ軸受は、図２に示す様に、テーパ状の内方軌
道１を有する外輪２と、テーパ状の外方軌道３を有し、
この外方軌道３の小径側端部に小鍔部４を、大径側端部
に大鍔部５をそれぞれ形成した内輪６と、保持器７によ
って上記内方軌道１と外方軌道３との間に保持案内され
る複数の円すいころ８、８とから構成している。2. Description of the Related Art Tapered roller bearings incorporating trapezoidal tapered rollers are capable of supporting radial loads and axial loads, and have a large withstand load. ing. As shown in FIG. 2, such a tapered roller bearing has an outer ring 2 having a tapered inner race 1 and a tapered outer race 3.
An inner race 6 having a small flange 4 at a small-diameter end of the outer race 3 and a large flange 5 at a large-diameter end thereof, and a retainer 7 for connecting the inner race 1 and the outer race 3 to each other. And a plurality of tapered rollers 8, 8 held and guided between them.
【０００３】この様な円すいころ軸受９は、例えば図３
に示す様に、外輪２をハウジング１０に内嵌し、内輪６
を軸１１に外嵌する事により、ハウジング１０の内周面
と軸１１の外周面との間に装着する。この様に円すいこ
ろ軸受９を装着した状態で、軸１１にラジアル方向或は
アキシャル方向の荷重が加わった場合、何れの方向の荷
重も円すいころ８、８により支承され、軸１１とハウジ
ング１０との相対的回転が円滑に行なわれる。[0003] Such a tapered roller bearing 9 is, for example, shown in FIG.
As shown in the figure, the outer race 2 is fitted inside the housing 10 and the inner race 6
Is fitted between the inner peripheral surface of the housing 10 and the outer peripheral surface of the shaft 11. When a radial or axial load is applied to the shaft 11 with the tapered roller bearing 9 mounted as described above, the load in any direction is supported by the tapered rollers 8 and 8, and the shaft 11 and the housing 10 are connected to each other. Relative rotation is smoothly performed.
【０００４】[0004]
【発明が解決しようとする課題】ところが、上述の様に
構成され使用される円すいころ軸受に於いては、従来次
に述べる様な不都合を生じた。即ち、円すいころ軸受９
を組み立てる場合、図４に示す様に、先ず保持器７によ
って保持された複数の円すいころ８、８と内輪６とを組
み合わせ、次いで上記複数の円すいころ８、８を外輪２
の内側に組み付ける様にしている。However, the tapered roller bearing constructed and used as described above has the following disadvantages. That is, the tapered roller bearing 9
As shown in FIG. 4, first, the plurality of tapered rollers 8, 8 held by the retainer 7 are combined with the inner ring 6, and then the plurality of tapered rollers 8, 8 are connected to the outer ring 2 as shown in FIG.
It is made to be assembled inside.
【０００５】保持器７によって保持された複数の円すい
ころ８、８と内輪６とを組み合わせる場合、小鍔部４を
下側にした状態で両部材８、６同士を組み合わせるが、
この際、複数の円すいころ８、８が保持器７の窓１３
（それぞれ１個ずつの円すいころ８を転動自在に保持す
る為、保持器７に形成した矩形の透孔）の内側で変位す
る。そして、複数の円すいころ８、８が正規の状態に整
列せず、しかも複数の円すいころ８、８と内輪６との関
係は、各円すいころ８、８の尾部側（小径側）端面が内
輪６の小鍔部４に当接し、各円すいころ８、８の頭部側
（大径側）端面と内輪６の大鍔部５との間に隙間１２が
存在した状態となる。この状態から、複数の円すいころ
８、８を外輪２の内側に組み付けた場合、図５に示す様
に、各円すいころ８、８の頭部側端面と内輪６の大鍔部
５との間に隙間１２が存在したままの状態に組み立てら
れる。When a plurality of tapered rollers 8, 8 held by a retainer 7 are combined with the inner ring 6, both members 8, 6 are combined with the small flange portion 4 being on the lower side.
At this time, the plurality of tapered rollers 8, 8
(Rectangular through holes formed in the holder 7 in order to hold one tapered roller 8 in a freely rolling manner). The plurality of tapered rollers 8, 8 are not aligned in a normal state, and the relationship between the plurality of tapered rollers 8, 8 and the inner ring 6 is such that the tail-side (small-diameter side) end face of each of the tapered rollers 8, 8 is an inner ring. 6, the gap 12 exists between the head-side (large-diameter side) end face of each of the tapered rollers 8, 8 and the large flange 5 of the inner ring 6. In this state, when a plurality of tapered rollers 8, 8 are assembled inside the outer ring 2, as shown in FIG. 5, the gap between the head-side end face of each tapered roller 8, 8 and the large flange 5 of the inner ring 6 is increased. Is assembled in a state where the gap 12 remains.
【０００６】円すいころ軸受９の使用状態に於いては、
図３に示す様に、各円すいころ８、８の頭部側端面が内
輪６の大鍔部５に当接する為、図５に示す様に、各円す
いころ８、８の頭部側端面と内輪６の大鍔部５との間に
隙間１２が存在した状態に組み立てられた円すいころ軸
受９を、図３に示す様にハウジング１０と軸１１との間
に組み付けて使用した場合、使用に伴なって各円すいこ
ろ８、８が、内輪６の大鍔部５に向けて移動する。In the use state of the tapered roller bearing 9,
As shown in FIG. 3, the head-side end faces of the tapered rollers 8, 8 come into contact with the large flange portion 5 of the inner ring 6, so that the head-side end faces of the tapered rollers 8, 8 are When the tapered roller bearing 9 assembled in a state where the gap 12 exists between the large collar portion 5 of the inner ring 6 and the housing 10 and the shaft 11 as shown in FIG. Accordingly, each tapered roller 8 moves toward the large collar portion 5 of the inner ring 6.
【０００７】この様に、外輪２と内輪６との間に設けた
複数の円すいころ８、８が大鍔部５に向け移動するのに
伴なって、各円すいころ８、８と外輪２の内方軌道１と
が当接する圧力が小さくなり、円すいころ軸受９の予圧
力が不足してしまう。この様な原因による予圧力不足の
発生を防止する為従来から、円すいころ軸受９をハウジ
ング１０と軸１１との間等に仮組み付けした後、ハウジ
ング１０と軸１１とを相対的に回転させる事により、円
すいころ軸受９の馴染み運転を行ない、円すいころ軸受
９を構成する複数の円すいころ８、８の頭部側端面を内
輪６の大鍔部５に当接させてから、円すいころ軸受９を
ハウジング１０と軸１１との間等に、本組み付けする
（予圧を付与する）事が行われている。As described above, as the plurality of tapered rollers 8, 8 provided between the outer ring 2 and the inner ring 6 move toward the large flange 5, the respective tapered rollers 8, 8 and the outer ring 2 The pressure with which the inner raceway 1 comes into contact is reduced, and the preload of the tapered roller bearing 9 is insufficient. In order to prevent the occurrence of insufficient preload due to such causes, conventionally, the tapered roller bearing 9 is temporarily assembled between the housing 10 and the shaft 11 or the like, and then the housing 10 and the shaft 11 are relatively rotated. As a result, the tapered roller bearing 9 performs a familiar operation, and the head-side end faces of the plurality of tapered rollers 8 constituting the tapered roller bearing 9 are brought into contact with the large flange portion 5 of the inner ring 6, and then the tapered roller bearing 9. Is mounted (provided with a preload) between the housing 10 and the shaft 11 or the like.
【０００８】ところが、従来の円すいころ軸受９の場
合、内輪６と複数の円すいころ８、８とを図４に示す様
に組み合わせた場合に、各円すいころ８、８の頭部側端
面と内輪６の大鍔部５との間に形成される隙間１２の寸
法が大きい為、上記馴染み運転を十分に（ハウジング１
０と軸１１との相対的回転を多く）しなければならず、
面倒であった。However, in the case of the conventional tapered roller bearing 9, when the inner ring 6 and a plurality of tapered rollers 8, 8 are combined as shown in FIG. 4, the head-side end face of each of the tapered rollers 8, 8 and the inner ring Since the size of the gap 12 formed between the large flange 5 and the large flange portion 6 is large, the above-described familiar operation can be sufficiently performed (the housing 1).
The relative rotation between 0 and axis 11)
It was troublesome.
【０００９】この様な事情に鑑みて、実公昭５８−５０
０９４号公報には、保持器を弾性を有する合成樹脂によ
り造り、この保持器の一部を小鍔部に対して突っ張らせ
る事により、円すいころの頭部側端面を大鍔部に押し付
ける構造が記載されている。この様な構造によれば、上
記馴染み運転を少なくしても、予圧力不足の発生を防止
できる。但し、この公報に記載された構造の場合には、
特殊な保持器を使用する為、部品の汎用性がなくてコス
トが嵩むだけでなく、上記保持器の一部と小鍔部とが摩
擦係合したままとなる為、回転トルクが大きくなった
り、運転時の発熱が多くなり易く、焼き付き等の故障が
発生し易くなるものと考えられる。又、上記保持器が破
損し易く、耐久性及び信頼性の面からも問題が多い。[0009] In view of such circumstances, Japanese Utility Model Publication No. 58-50
No. 094 discloses a structure in which a retainer is made of a synthetic resin having elasticity, and a part of the retainer is pressed against a small flange to press a tapered roller head side end face against a large flange. Are listed. According to such a structure, it is possible to prevent the occurrence of insufficient preload even if the familiar operation is reduced. However, in the case of the structure described in this publication,
The use of a special retainer not only increases the cost because there is no versatility of parts, but also increases the rotational torque because a part of the retainer and the small flange remain frictionally engaged. It is considered that heat generation during operation is likely to increase and failures such as burn-in are likely to occur. Further, the cage is easily broken, and there are many problems in terms of durability and reliability.
【００１０】更に、上記公報に記載された発明の場合に
は、金属に比べて耐熱性及び耐薬品性が劣る、合成樹脂
製の保持器を使用する為、高温下での使用はできず、使
用可能な潤滑剤の種類も限定される等、用途が限定され
る事が避けられない。又、使用可能な潤滑剤にしても、
上記保持器が摩耗する事により生じた摩耗粉がこの潤滑
剤を汚染する事が考えられ、やはり、耐久性、信頼性の
面から問題を生じる。更に、常に内輪と擦れ合ったまま
となる合成樹脂製の保持器が摩耗する為、保守・点検の
為に分解した後、再組立を行なう際には、この保持器を
交換する必要が生じ、保守・点検に要するコストが嵩
む。更には、合成樹脂製の保持器の一部を内輪外周面の
小鍔部に対して突っ張らせる必要上、この内輪の幅を、
本来円すいころ軸受を構成する為に必要とする以上に大
きくしなければならず、円すいころ軸受が大型化する。
本発明は、上述の様な不都合を何れも解消できる円すい
ころ軸受を提供するものである。Further, in the case of the invention described in the above-mentioned publication, since a cage made of synthetic resin, which is inferior to metal in heat resistance and chemical resistance, is used, it cannot be used at high temperatures. It is unavoidable that the use is limited, for example, the type of lubricant that can be used is also limited. In addition, even if it can be used lubricant,
It is conceivable that abrasion powder generated by abrasion of the retainer contaminates the lubricant, which also causes a problem in terms of durability and reliability. Furthermore, since the synthetic resin retainer that always keeps rubbing against the inner ring wears out, it is necessary to replace the retainer when reassembling after disassembly for maintenance and inspection. Costs for maintenance and inspection increase. Furthermore, since it is necessary to make a part of the retainer made of synthetic resin project against the small flange portion on the outer peripheral surface of the inner ring, the width of the inner ring is
The size of the tapered roller bearing must be larger than necessary to construct the tapered roller bearing, and the size of the tapered roller bearing increases.
The present invention provides a tapered roller bearing capable of solving any of the above-mentioned disadvantages.
【００１１】[0011]
【課題を解決する為の手段】本発明の円すいころ軸受
は、テーパ状の内方軌道を有する外輪と、テーパ状の外
方軌道を有し、この外方軌道の小径側端部に小鍔部を、
大径側端部に大鍔部をそれぞれ形成した内輪と、保持器
によって上記内方軌道と外方軌道との間に保持案内され
る複数の円すいころとから構成される。特に、本発明の
円すいころ軸受に於いては、上記各円すいころを内輪の
外方軌道上の正規位置に配列し、且つ各円すいころの尾
部側と小鍔部とを接触させた場合に、各円すいころの頭
部側端面と大鍔部との間に形成される隙間の寸法△Ｌ
を、０．２mm以下としている。A tapered roller bearing according to the present invention has an outer ring having a tapered inner race and a tapered outer race, and a small flange is provided at a small-diameter end of the outer race. Department
It is composed of an inner ring having a large flange formed at the large diameter end, and a plurality of tapered rollers which are held and guided between the inner and outer races by a retainer. In particular, in the tapered roller bearing of the present invention, when each of the tapered rollers is arranged at a regular position on the outer track of the inner ring, and when the tail side of each tapered roller is brought into contact with the small flange, The dimension ΔL of the gap formed between the head end surface of each tapered roller and the large flange.
Is set to 0.2 mm or less.
【００１２】[0012]
【作用】上述の様に構成する本発明の円すいころ軸受を
ハウジングと軸との間等に装着し、両部材の相対的回転
を自在とすると共に、両部材の間に働くラジアル方向の
荷重とアキシャル方向の荷重とを支承する際の作用自体
は、前述した従来からの円すいころ軸受と同様である。
特に、本発明の円すいころ軸受の場合、円すいころの頭
部側端面と大鍔部との間に形成される隙間の寸法△Ｌを
小さくしている為、この円すいころ軸受をハウジングと
軸との間等に組み付けた後、ころの頭部側端面と大鍔部
とを当接させる迄に要する馴染み運転が短いもので済
み、円すいころ軸受に十分な予圧を付与する作業が容易
になる。The tapered roller bearing of the present invention constructed as described above is mounted between the housing and the shaft, so that the two members can rotate freely, and the radial load acting between the two members can be reduced. The operation itself in supporting the load in the axial direction is the same as that of the conventional tapered roller bearing described above.
In particular, in the case of the tapered roller bearing of the present invention, the dimension ΔL of the gap formed between the head-side end face of the tapered roller and the large flange portion is reduced, so that the tapered roller bearing is connected to the housing and the shaft. After assembling between the rollers, the running-in operation required for bringing the head side end surface of the roller into contact with the large flange portion is short, and the operation of applying a sufficient preload to the tapered roller bearing is facilitated.
【００１３】又、保持器を使用する場合も、この保持器
は一般的なもので足りる。しかも、馴染み運転を終了し
た後予圧を付与した状態では、従来から一般的に知られ
ている円すいころ軸受と同じ様に機能して、保持器が内
輪の一部と擦れ合う事もない。この為、コストが増大し
たり、或は回転トルクや発熱量の増大を招く事もない。
従って、保持器の性状に基づいて円すいころ軸受の用途
が限定される事がなく、信頼性及び耐久性の確保も容易
である。又、保持器を組み込む為に、内輪の幅を必要以
上に大きくする必要もない為、円すいころ軸受の小型・
軽量化も容易である。When a cage is used, a general one is sufficient. In addition, in a state in which the preload is applied after the familiar operation is completed, the retainer functions in the same manner as a conventionally generally known tapered roller bearing, and the retainer does not rub against a part of the inner ring. Therefore, there is no increase in cost or increase in rotational torque or heat generation.
Therefore, the use of the tapered roller bearing is not limited based on the properties of the cage, and the reliability and durability can be easily secured. Also, it is not necessary to increase the width of the inner ring more than necessary to incorporate the cage.
Lightening is also easy.
【００１４】[0014]
【実施例】次に、本発明の効果を確認する為に行った実
験に就いて説明しつつ、本発明を更に詳しく説明する。
本発明の円すいころ軸受９は、図１〜２に示す様に、テ
ーパ状の内方軌道１を有する外輪２と、テーパ状の外方
軌道３を有し、この外方軌道３の小径側端部に小鍔部４
を、大径側端部に大鍔部５をそれぞれ形成した内輪６
と、保持器７によって上記内方軌道１と外方軌道３との
間に保持案内される複数の円すいころ８、８とから構成
している。Next, the present invention will be described in more detail while describing experiments conducted for confirming the effects of the present invention.
The tapered roller bearing 9 of the present invention has an outer race 2 having a tapered inner race 1 and a tapered outer race 3 as shown in FIGS. Small collar 4 at the end
And an inner ring 6 having a large flange 5 formed at the large diameter end.
And a plurality of tapered rollers 8, 8 which are held and guided between the inner track 1 and the outer track 3 by a retainer 7.
【００１５】そして、保持器７は金属製で、各円すいこ
ろ８、８の投影面積よりも小さな窓１３、１３を形成し
た篭形保持器としており、この保持器７を、各円すいこ
ろ８、８のピッチ円径よりも大径としている。この結
果、保持器７により保持された複数の円すいころ８、８
を内輪６の外側に装着した場合、これら複数の円すいこ
ろ８、８は内輪６と分離する事なく、両部材６、８を一
体的に取り扱える状態となる。The cage 7 is made of metal and is a cage-type cage in which windows 13, 13 smaller than the projected area of the tapered rollers 8, 8, are formed. 8 is larger than the pitch circle diameter. As a result, the plurality of tapered rollers 8, 8 held by the holder 7
Is mounted on the outer side of the inner ring 6, the plurality of tapered rollers 8, 8 are not separated from the inner ring 6, so that the two members 6, 8 can be integrally handled.
【００１６】本発明の円すいころ軸受９は、図１に示す
様に、円すいころ８を内輪６の外方軌道３上の正規位置
に配列し、且つ各円すいころ８の尾部側と小鍔部４とを
接触させた場合に各円すいころ８の頭部側端面と大鍔部
５との間に形成される、隙間１２の寸法△Ｌを規制して
いる。即ち、本発明の場合、上記隙間１２の寸法△Ｌを
０．２mm以下（△Ｌ≦０．２mm）としている。これに対
して、従来の円すいころ軸受の場合、上記隙間１２の寸
法△Ｌは０．４〜０．６mm程度であった。In the tapered roller bearing 9 of the present invention, as shown in FIG. 1, the tapered rollers 8 are arranged at regular positions on the outer raceway 3 of the inner ring 6, and the tail side of each tapered roller 8 and the small flange portion. 4, the dimension ΔL of the gap 12 formed between the head-side end face of each tapered roller 8 and the large flange portion 5 is regulated. That is, in the case of the present invention, the dimension ΔL of the gap 12 is set to 0.2 mm or less (ΔL ≦ 0.2 mm). On the other hand, in the case of the conventional tapered roller bearing, the dimension ΔL of the gap 12 is about 0.4 to 0.6 mm.
【００１７】次に、上述の様に、円すいころ８を内輪６
の外方軌道３上の正規位置に配列し、且つ各円すいころ
８の尾部側と小鍔部４とを接触させた場合に、各円すい
ころ８の頭部側端面と大鍔部５との間に形成される隙間
１２の寸法△Ｌを、０．２mm以下とした場合の効果を確
認する為に行なった実験に就いて説明する。Next, as described above, the tapered rollers 8 are connected to the inner ring 6.
When the tail side of each tapered roller 8 and the small flange 4 are brought into contact with each other at a regular position on the outer orbit 3 of the tapered roller 3, the head side end face of each tapered roller 8 and the large flange 5 An experiment performed to confirm the effect when the dimension ΔL of the gap 12 formed therebetween is set to 0.2 mm or less will be described.
【００１８】実験は、図５に示す様に、各円すいころ
８、８の頭部側端面と内輪６の大鍔部５とが当接しない
状態に組み立てられた円すいころ軸受９を、外輪２を固
定する事により、同図に示した様に水平に保持し、内輪
６を回転させたり、或は往復揺動させる事に伴なう内輪
６の変位量を測定する事で行なった。即ち、図５に示す
様な状態に組み立てられた円すいころ軸受９を運転した
場合、内輪６の運動に伴なってこの内輪６が徐々に下降
するが、この下降量を内輪６の変位量として測定し、記
録した。実験は、本発明品として、上記隙間１２の寸法
△Ｌが０．１３mmのものを２個、従来品として、上記隙
間１２の寸法△Ｌが０．５５〜０．６０mmのものを２
個、それぞれ使用した。In the experiment, as shown in FIG. 5, the tapered roller bearing 9 assembled in such a manner that the head-side end faces of the tapered rollers 8, 8 do not come into contact with the large flange portion 5 of the inner ring 6 is mounted on the outer ring 2, By fixing the inner ring 6 as shown in the figure, the inner ring 6 was held horizontally, and the amount of displacement of the inner ring 6 due to the rotation of the inner ring 6 or the reciprocating swing was measured. That is, when the tapered roller bearing 9 assembled in the state as shown in FIG. 5 is operated, the inner ring 6 gradually descends with the movement of the inner ring 6, and the amount of the decrease is defined as the displacement amount of the inner ring 6. Measured and recorded. In the experiment, two products of the present invention having the gap 12 having a dimension ΔL of 0.13 mm and two conventional products having a dimension ΔL of the gap 12 of 0.55 to 0.60 mm were used.
And each was used.
【００１９】先ず、第一の実験は、内輪６を一方向に回
転させると共に、回転に伴なってこの内輪６が下降する
変位量を、回転回数との関係で記録した。この結果、本
発明品の場合、内輪６の変位量は、回転回数との関係で
図６の破線ａ、ｂに示す様に変化したのに対し、従来品
の場合同図に実線ｃ、ｄで示す様に変化した。First, in the first experiment, the inner ring 6 was rotated in one direction, and the amount of displacement of the inner ring 6 descending with the rotation was recorded in relation to the number of rotations. As a result, in the case of the product of the present invention, the displacement amount of the inner ring 6 changed as shown by broken lines a and b in FIG. 6 in relation to the number of rotations, whereas in the case of the conventional product, the solid lines c and d in FIG. It changed as shown by.
【００２０】又、第二の実験は、内輪６を３０度ずつ往
復揺動させ、揺動に伴なってこの内輪６が下降する変位
量を、揺動回数との関係で記録した。この結果、本発明
品の場合、内輪６の変位量は、揺動回数との関係で図７
の破線ｅ、ｆに示す様に変化したのに対し、従来品の場
合、同図に実線ｇ、ｈで示す様に変化した。In the second experiment, the inner ring 6 was reciprocated by 30 degrees each time, and the amount of displacement of the inner ring 6 descending with the rocking was recorded in relation to the number of times of rocking. As a result, in the case of the product of the present invention, the displacement amount of the inner ring 6 depends on the number of swings as shown in FIG.
In contrast, in the case of the conventional product, it changed as shown by the solid lines g and h in FIG.
【００２１】これら図６〜７から明らかな通り、本発明
の円すいころ軸受９の場合、馴染み運転に伴なう内輪６
の変位量が少なく、しかも早期に安定状態（各円すいこ
ろ８、８の頭部側端面と内輪６の大鍔部５とが当接し、
それ以上内輪６が変位しない状態）に達する事が解る。As is apparent from FIGS. 6 and 7, in the case of the tapered roller bearing 9 of the present invention, the inner ring 6 accompanying the familiar operation is used.
Is small, and is in a stable state at an early stage (the end faces on the head side of the tapered rollers 8, 8 come into contact with the large flange 5 of the inner ring 6,
(The state in which the inner ring 6 is not further displaced).
【００２２】更に、第三の実験として、上記隙間１２の
寸法△Ｌが少しずつ異なる複数の円すいころ軸受９を使
用して、これらの馴染み運転を行ない、安定状態に達す
る迄に内輪６を回転させた回数を測定した所、図８に示
した様な結果を得られた。この図８から明らかな通り、
上記隙間１２の寸法△Ｌが０．２mm以下であった場合、
馴染み運転の回数は同じ様に少なくて済むが、上記隙間
１２の寸法△Ｌが０．２mmを越えた場合（△Ｌ＞０．２
mm）、必要とする馴染み運転の回数が次第に多くなる。Further, as a third experiment, a plurality of tapered roller bearings 9 each having a slightly different dimension ΔL of the gap 12 are used, and the familiar operation is performed to rotate the inner ring 6 until a stable state is reached. When the number of times of the operation was measured, a result as shown in FIG. 8 was obtained. As is clear from FIG.
When the dimension ΔL of the gap 12 is 0.2 mm or less,
The number of times of the familiar operation can be reduced similarly, but when the size ΔL of the gap 12 exceeds 0.2 mm (ΔL> 0.2
mm), the number of required familiar operations increases gradually.
【００２３】[0023]
【発明の効果】本発明の円すいころ軸受は、以上に述べ
た通り構成され作用するが、簡単な構成で製作費を高く
する事もなく、しかも十分な予圧を保つ為に要する馴染
み運転も少なくて済む為、円すいころ軸受を組み込んだ
機械装置の組み立て作業の能率化を図る事ができる。し
かも、回転トルクが小さく発熱量も少ない、安価な、あ
らゆる用途に使用して十分な耐久性及び信頼性を確保で
きる円すいころ軸受を実現できる。The tapered roller bearing of the present invention is constructed and operates as described above. However, the simple construction does not increase the manufacturing cost, and the running-in operation required for maintaining a sufficient preload is small. As a result, the assembling work of the machine incorporating the tapered roller bearing can be made more efficient. In addition, it is possible to realize a tapered roller bearing which has a small rotating torque and a small amount of heat generation, is inexpensive, can be used for all purposes, and can secure sufficient durability and reliability.
【図１】本発明の円すいころ軸受を説明する為の部分断
面図。FIG. 1 is a partial sectional view for explaining a tapered roller bearing of the present invention.
【図２】本発明の対象となる円すいころ軸受の一部切断
斜視図。FIG. 2 is a partially cut perspective view of a tapered roller bearing to which the present invention is applied.
【図３】円すいころ軸受の使用状態の１例を示す断面
図。FIG. 3 is a sectional view showing an example of a usage state of the tapered roller bearing.
【図４】円すいころ軸受を組み立てる状態を工程の初期
状態で示す断面図。FIG. 4 is a sectional view showing a state in which the tapered roller bearing is assembled in an initial state of a process.
【図５】同じく終期状態で示す断面図。FIG. 5 is a sectional view showing the terminal device in the final state.
【図６】本発明の効果を確認する為に行なった第一の実
験の結果を示す線図。FIG. 6 is a diagram showing the results of a first experiment performed to confirm the effects of the present invention.
【図７】同じく第二の実験の結果を示す線図。FIG. 7 is a diagram showing the results of the second experiment.
【図８】 同じく第三の実験の結果を示す線図。 １ 内方軌道 ２ 外輪 ３ 外方軌道 ４ 小鍔部 ５ 大鍔部 ６ 内輪 ７ 保持器 ８ 円すいころ ９ 円すいころ軸受 １０ ハウジング １１ 軸 １２ 隙間 １３ 窓FIG. 8 is a diagram showing the results of the third experiment. DESCRIPTION OF SYMBOLS 1 Inner raceway 2 Outer race 3 Outer raceway 4 Small flange 5 Large flange 6 Inner ring 7 Cage 8 Tapered roller 9 Tapered roller bearing 10 Housing 11 Shaft 12 Clearance 13 Window
───────────────────────────────────────────────────── フロントページの続き (56)参考文献 実公 昭58−50094（ＪＰ，Ｙ２) 特公 昭46−25202（ＪＰ，Ｂ１) (58)調査した分野(Int.Cl.7，ＤＢ名) F16C 19/36 F16C 33/46 F16C 33/58 ──────────────────────────────────────────────────続 き Continuation of the front page (56) References Jikken Sho 58-50094 (JP, Y2) Japanese Patent Publication No. 46-25202 (JP, B1) (58) Fields investigated (Int. Cl. 7 , DB name) F16C 19/36 F16C 33/46 F16C 33/58
Claims (2)
ーパ状の外方軌道を有し、この外方軌道の小径側端部に
小鍔部を、大径側端部に大鍔部をそれぞれ形成した内輪
と、保持器によって上記内方軌道と外方軌道との間に保
持案内される複数の円すいころとから成る円すいころ軸
受に於いて、円すいころを内輪の外方軌道上の正規位置
に配列し、且つ各円すいころの尾部側と小鍔部とを接触
させた場合に各円すいころの頭部側端面と大鍔部との間
に形成される隙間の寸法△Ｌを、０．２mm以下とした事
を特徴とする円すいころ軸受。1. An outer race having a tapered inner race, a tapered outer race, a small flange portion at a small-diameter side end of the outer race, and a large flange portion at a large-diameter side end. In the tapered roller bearing consisting of an inner ring each formed and a plurality of tapered rollers held and guided between the inner race and the outer race by a retainer, the tapered rollers are arranged on the outer race of the inner race. Arranged at the regular position, and when the tail side of each tapered roller and the small flange contact, the dimension ΔL of the gap formed between the head side end surface of each tapered roller and the large flange, Tapered roller bearings characterized by 0.2 mm or less.
面積よりも小さな窓を形成した篭形保持器であり、この
保持器が各円すいころのピッチ円径よりも大径である、
請求項１に記載の円すいころ軸受。2. A cage-shaped cage, wherein the cage is made of metal and has a window smaller than a projected area of each tapered roller, and the cage has a diameter larger than a pitch circle diameter of each tapered roller.
The tapered roller bearing according to claim 1.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP10206151A JP3039638B2 (en) | 1998-07-22 | 1998-07-22 | Tapered roller bearing |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP10206151A JP3039638B2 (en) | 1998-07-22 | 1998-07-22 | Tapered roller bearing |
Related Parent Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP1076764A Division JP2844648B2 (en) | 1989-03-30 | 1989-03-30 | Tapered roller bearing |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPH1182490A JPH1182490A (en) | 1999-03-26 |
| JP3039638B2 true JP3039638B2 (en) | 2000-05-08 |
Family
ID=16518650
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP10206151A Expired - Fee Related JP3039638B2 (en) | 1998-07-22 | 1998-07-22 | Tapered roller bearing |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JP3039638B2 (en) |
Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2002130287A (en) * | 2000-10-30 | 2002-05-09 | Nsk Ltd | Cone roller bearing |
-
1998
- 1998-07-22 JP JP10206151A patent/JP3039638B2/en not_active Expired - Fee Related
Also Published As
| Publication number | Publication date |
|---|---|
| JPH1182490A (en) | 1999-03-26 |
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