JPH0217243Y2 - - Google Patents
Info
- Publication number
- JPH0217243Y2 JPH0217243Y2 JP1985065780U JP6578085U JPH0217243Y2 JP H0217243 Y2 JPH0217243 Y2 JP H0217243Y2 JP 1985065780 U JP1985065780 U JP 1985065780U JP 6578085 U JP6578085 U JP 6578085U JP H0217243 Y2 JPH0217243 Y2 JP H0217243Y2
- Authority
- JP
- Japan
- Prior art keywords
- gear
- bearing
- outer ring
- depth
- ring raceway
- 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
Links
- 230000005540 biological transmission Effects 0.000 claims description 13
- 238000010438 heat treatment Methods 0.000 description 4
- 239000010802 sludge Substances 0.000 description 3
- 238000005336 cracking Methods 0.000 description 2
- 238000003754 machining Methods 0.000 description 2
- 150000001875 compounds Chemical class 0.000 description 1
- 238000005261 decarburization Methods 0.000 description 1
- 230000007423 decrease Effects 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- 238000002474 experimental method Methods 0.000 description 1
- 238000000034 method Methods 0.000 description 1
- 238000005498 polishing Methods 0.000 description 1
- 238000005096 rolling process Methods 0.000 description 1
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
- F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
- F16C33/30—Parts of ball or roller bearings
- F16C33/58—Raceways; Race rings
- F16C33/583—Details of specific parts of races
- F16C33/585—Details of specific parts of races of raceways, e.g. ribs to guide the rollers
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- 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
- F16C19/383—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 with tapered rollers, i.e. rollers having essentially the shape of a truncated cone
- F16C19/385—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 with tapered rollers, i.e. rollers having essentially the shape of a truncated cone with two rows, i.e. double-row tapered roller bearings
- F16C19/386—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 with tapered rollers, i.e. rollers having essentially the shape of a truncated cone with two rows, i.e. double-row tapered roller bearings in O-arrangement
-
- 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
- F16C19/44—Needle bearings
- F16C19/48—Needle bearings with two or more rows of needles
-
- 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
- F16C19/54—Systems consisting of a plurality of bearings with rolling friction
- F16C19/55—Systems consisting of a plurality of bearings with rolling friction with intermediate floating or independently-driven rings rotating at reduced speed or with other differential ball or roller bearings
-
- 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
- F16C23/088—Ball or roller bearings self-adjusting by means of crowning
-
- 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
- F16C2361/00—Apparatus or articles in engineering in general
- F16C2361/61—Toothed gear systems, e.g. support of pinion shafts
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Details Of Gearings (AREA)
Description
【考案の詳細な説明】
〔産業上の利用分野〕
本考案は、伝動装置の軸受装置とくに自動車用
トランスミツシヨンの軸受装置に関する。[Detailed Description of the Invention] [Industrial Field of Application] The present invention relates to a bearing device for a power transmission, and particularly to a bearing device for an automobile transmission.
トラツクや乗用車のトランスミツシヨンは、近
年四輪駆動車の割合が増えまたそれによる軽量化
に伴つて軸受スペースが狭小化する一方、伝達す
べきトルクの上昇につれて軸受容量のアツプが求
められている。そこで、これらの要求に応えるた
め、ギヤーとシヤフトおよび軸受の一体化が考慮
され始めている。
In the transmissions of trucks and passenger cars, the proportion of four-wheel drive vehicles has increased in recent years, and as the weight has been reduced, the bearing space has become narrower.At the same time, as the torque to be transmitted increases, there is a need for an increase in bearing capacity. . Therefore, in order to meet these demands, consideration has begun to be given to integrating gears, shafts, and bearings.
例えば、或る四輪駆動車は、機関に連結された
主軸から、これと平行に設置したギヤ付き中空シ
ヤフト、シヤフトに取り付けたセンターデフ、中
空シヤフトと同心に設置したピニオンシヤフトお
よびプロペラシヤフトを経て、前輪および後輪を
駆動するようになつており、この伝動装置におい
ては、軸受スペースを節約するため、中空シヤフ
トの前端を支持する円錐ころ軸受は中空シヤフト
の内径に外輪軌道を直接加工されている。 For example, a four-wheel drive vehicle has a main shaft connected to the engine, a hollow shaft with gears installed parallel to the main shaft, a center differential attached to the shaft, a pinion shaft and a propeller shaft installed concentrically with the hollow shaft. , which drives the front and rear wheels, and in this transmission, in order to save bearing space, the tapered roller bearing that supports the front end of the hollow shaft has an outer ring raceway directly machined on the inside diameter of the hollow shaft. There is.
また、トランスミツシヨン用の各種ギヤにおい
ても、同様にギヤの内径に軸受を取り付ける場合
に、従来の軸受外輪を省略する傾向が広がつてい
る。 Furthermore, in various gears for transmissions, there is a growing trend to omit the conventional bearing outer ring when a bearing is similarly attached to the inner diameter of the gear.
上記のような乗用車やトラツクのギヤまたはギ
ヤ付き中空シヤフトにおいて、ギヤはほとんどが
滲炭熱処理されており、その滲炭深さは0.2〜1.0
mm程度である。一方、ころ軸受の滲炭深さは0.8
〜1.4mm程度は必要である。
In the gears or geared hollow shafts of passenger cars and trucks mentioned above, most of the gears are subjected to charring heat treatment, and the charring depth is 0.2 to 1.0.
It is about mm. On the other hand, the charring depth of roller bearings is 0.8
~1.4mm is required.
そこでギヤボスの内周に円錐ころ軸受の外輪軌
道を直接加工する場合、ギヤの滲炭深さをころ軸
受に適した0.8〜１mm程度の深さにしようとすれ
ば、ギヤの歯に割れが生じ易くなるとともに、滲
炭深さの自乗に比例する熱処理時間の延長に従つ
て熱処理費用が増大し、強度とコストの問題が生
じてくる。 Therefore, when machining the outer ring raceway of a tapered roller bearing directly on the inner periphery of the gear boss, if you try to set the deburring depth of the gear to a depth of about 0.8 to 1 mm, which is suitable for roller bearings, cracks will occur in the gear teeth. At the same time, as the heat treatment time increases in proportion to the square of the decoal depth, the heat treatment cost increases, resulting in strength and cost problems.
と言つて、ギヤ滲炭深さを現状の0.2〜1.0mm程
度とし、直接ころ軸受の外輪軌道として使用する
と、滲炭深さが浅いために、外輪の寿命が低下し
ひいては軸受全体の寿命が低下することになる。 However, if the gear charring depth is set at the current level of 0.2 to 1.0 mm and used as the outer ring raceway of a direct roller bearing, the shallow charring depth will shorten the life of the outer ring and, in turn, the life of the entire bearing. This will result in a decline.
本考案は、ギヤボス内径に直接加工してころ軸
受外輪軌道とする場合、滲炭深さをギヤに現状の
適した0.2〜1.0mmのままとすることのできる、ト
ランスミツシヨン用軸受を提供することを目的と
している。 The present invention provides a bearing for a transmission in which when the outer ring raceway of a roller bearing is made by directly machining the inner diameter of a gear boss, the deburring depth can be kept at 0.2 to 1.0 mm, which is currently suitable for the gear. The purpose is to
本考案者は、種々実験、研究の結果、ころ軸受
の外輪となるギヤボス内径に、滲炭処理後研磨加
工により軌道にクラウニングを施すことにより、
軌道に生じるエツジロードを小さくして滲炭深さ
を現状のギヤの滲炭深さと同じにしても、ころ軸
受に適する程度に滲炭深さを深くした時と同じ位
の長い期間、軸受の機能を十分に発揮することが
できることを確認した。
As a result of various experiments and research, the inventor of the present invention determined that by crowning the inner diameter of the gear boss, which is the outer ring of the roller bearing, by polishing the raceway after decarburizing the inner diameter,
Even if the edge load generated on the raceway is reduced and the sludge depth is the same as the current sludge depth of the gear, the bearing will not function for as long as when the sludge depth is increased to a level suitable for roller bearings. It was confirmed that it was possible to fully demonstrate the
従つて、本考案は、上記問題点を解決する手段
として、ギヤボス内径にころ軸受の外輪軌道を直
接設けるとともに、ギヤと外輪軌道とにそれぞれ
適した深さの滲炭を施したトランスミツシヨンの
軸受装置において、前記ギヤボス内径の外輪軌道
に施される滲炭の深さがギヤに施される滲炭の深
さと同一とされ、かつこの外輪軌道にクラウニン
グが施されたトランスミツシヨンの軸受装置を提
供するもので、これにより、ギヤの割れを防止す
るとともに、軸受の寿命を延長することができ
る。 Therefore, as a means to solve the above-mentioned problems, the present invention provides a transmission in which the outer ring raceway of the roller bearing is directly provided on the inner diameter of the gear boss, and the gear and outer ring raceway are respectively blotted to appropriate depths. A bearing device for a transmission in which the depth of the charring applied to the outer ring raceway of the inner diameter of the gear boss is the same as the depth of the charring applied to the gear, and the outer ring raceway is crowned. This prevents gear cracking and extends the life of the bearing.
以下、図面を参照して、本考案の実施例を説明
する。
Embodiments of the present invention will be described below with reference to the drawings.
本考案者は、上記のように、負荷とクラウニン
グの施し方を種々に変えてテストしてみたとこ
ろ、下記のような結果を得た。 The present inventor conducted tests with various loads and crowning methods as described above, and obtained the following results.
１ 負荷が軸受定格荷重の25％以下のときには、
第１図ａに示すように、ころの転走幅Ｌ全体に
わたつて同一半径Ｒ（＝L2／0.08）の円弧で形
成されるクラウニングを施すのが好ましい。1 When the load is less than 25% of the bearing rated load,
As shown in FIG. 1a, it is preferable to provide a crowning formed by an arc having the same radius R (=L 2 /0.08) over the entire rolling width L of the roller.
２ 負荷が、軸受定格荷重の25〜80％のときに
は、第１図ｂに示すように、中央部分L′＝３／
４〜２／3Lにわたつて平坦部を残した、ｈ＝
0.010〜0.025mmの高さの台型のクラウニングを
施すのが好ましい。2 When the load is 25 to 80% of the bearing rated load, the central part L' = 3/3 as shown in Figure 1b.
Leaving a flat part over 4 to 2/3L, h=
Preferably, a trapezoidal crowning with a height of 0.010 to 0.025 mm is applied.
３ 負荷が、軸受定格荷重の80％以上のときに
は、第１図ｃに示すように、中央部L′＝２／
3Lが一定半径Ｒ（L2／0.12）の円弧で形成され
る高さがｈ＝0.020〜0.035mmの複合クラウニン
グを施すのが好ましい。3 When the load is 80% or more of the bearing rated load, the center part L' = 2/
It is preferable to apply compound crowning where 3L is formed by a circular arc with a constant radius R (L 2 /0.12) and the height is h = 0.020 to 0.035 mm.
すなわち、クラウニング量が一定であれば、負
荷が大きくなるほど、ころのエツジロードも大き
くなるので、負荷に合わせてクラウニング量（特
に軌道の両端部分）を大きくして、上記エツジロ
ードを小さくし、軌道に生じる局部的な応力集中
を低減させ、軌道の滲炭を施した部分に均等に応
力が分散するようにして、浅い滲炭深さでも十分
に負荷を受けられるようにしなければならないと
いうことである。 In other words, if the amount of crowning is constant, the larger the load, the larger the edge load on the rollers. Therefore, the amount of crowning (especially at both ends of the raceway) is increased in accordance with the load to reduce the edge load generated on the raceway. This means that it is necessary to reduce local stress concentration and distribute the stress evenly over the decarburized portion of the raceway, so that even a shallow decarburization depth can sufficiently receive the load.
以下これらのクラウニングを施した各種のギヤ
を例示する。 Examples of various types of gears with these crownings are shown below.
第２図は、乗用車ATXのアイドラギヤに適用
したもので、ギヤ１はそのボス部に、２個の単列
円錐ころ軸受が取付けられている。ギヤボス内径
６にはクラウニングが施され、円錐ころ２，３が
それぞれ内輪軌道となる内輪４，５とともに両側
から挿入される。 Fig. 2 shows an application to the idler gear of an ATX passenger car, in which gear 1 has two single-row tapered roller bearings attached to its boss. The gear boss inner diameter 6 is crowned, and the tapered rollers 2 and 3 are inserted from both sides together with the inner rings 4 and 5 that serve as inner raceways.
第３図は、大型トラツク、トランスミツシヨン
のリバースギヤ用の円筒ころ軸受に適用したもの
で、両端に１個づつのギヤを有する円筒型のリバ
ースギヤ１は、同じく両端の円筒ころ軸受２，３
により固定シヤフト７に取付けられている。 Fig. 3 shows a cylindrical roller bearing applied to a reverse gear of a large truck or transmission. 3
It is attached to the fixed shaft 7 by.
リバースギヤ１の両端部には円筒ころ２，３を
受け入れるためのボス孔が設けられ、円筒ころに
対する外輪軌道となるその内径６には、クラウニ
ングが施される。 Boss holes for receiving cylindrical rollers 2 and 3 are provided at both ends of the reverse gear 1, and the inner diameter 6 of the reverse gear 1, which serves as an outer ring raceway for the cylindrical rollers, is crowned.
第４図は、大型トラツク、トランスミツシヨン
パイロツト軸受に適用したもので、メインドライ
ブシヤフト８の一端に形成されたメインドライブ
ギヤ１は、ボス部に、メインシヤフト１０の一端
に嵌装されたパイロツト（ころ）軸受２を挿入さ
れ、メインドライブシヤフト８はメインドライブ
軸受９により、ケースに支持されている。メイン
ドライブ１の側方には、メインドライブシヤフト
８とメインシヤフト１０とを係脱するためシヤフ
ト１０に支持されたスリーブ１１が設置されてい
る。メインドライブギヤ１のボス内径６はパイロ
ツト軸受２の外輪を形成し、滲炭処理軸クラウニ
ングを施される。 Fig. 4 shows a transmission pilot bearing applied to a large truck and a transmission pilot bearing, in which a main drive gear 1 formed at one end of a main drive shaft 8 is attached to a boss portion of a pilot shaft fitted to one end of a main shaft 10. A (roller) bearing 2 is inserted, and the main drive shaft 8 is supported by the case by a main drive bearing 9. A sleeve 11 supported by the shaft 10 is installed on the side of the main drive 1 to engage and disengage the main drive shaft 8 and the main shaft 10. The inner diameter 6 of the boss of the main drive gear 1 forms the outer ring of the pilot bearing 2, and is provided with a decarburized shaft crowning.
本考案により、ギヤ及び外輪軌道に施す滲炭の
深さをギヤに適した深さにすることができるた
め、ギヤの割れを防止することができるともに熱
処理に要する費用を削減することができ、かつ外
側軌道にクラウニングを施すことにより軸受の寿
命を向上することができ、しかも同一スペースで
の軸受の小型化、軽量化を達成することができ
る。
With this invention, the depth of the decharring applied to the gear and outer ring raceway can be adjusted to a depth suitable for the gear, making it possible to prevent cracking of the gear and reduce the cost required for heat treatment. Furthermore, by crowning the outer raceway, the life of the bearing can be extended, and moreover, the bearing can be made smaller and lighter in the same space.
第１図ａ，ｂ，ｃは本考案によるギヤボスの３
種のクラウニングの断面図。第２図ないし第４図
は、上記クラウニングを施した各種のギヤの断面
図。
１……ギヤ、２，３……ころ軸受、４，５……
軸受内輪、６……ボス内径、７……固定シヤフ
ト、８……メインドライブシヤフト、９……メイ
ンドライブ軸受、１０……メインシヤフト、１１
……スリーブ。
Figure 1 a, b, and c are three gear bosses according to the present invention.
Cross section of crowning of seeds. FIGS. 2 to 4 are cross-sectional views of various gears provided with the above-mentioned crowning. 1... Gear, 2, 3... Roller bearing, 4, 5...
Bearing inner ring, 6... Boss inner diameter, 7... Fixed shaft, 8... Main drive shaft, 9... Main drive bearing, 10... Main shaft, 11
……sleeve.
Claims (1)
るとともに、ギヤと外輪軌道とにそれぞれ適した
深さの滲炭を施したトランスミツシヨンの軸受装
置において、前記ギヤボス内径の外輪軌道に施さ
れる滲炭の深さがギヤに施される滲炭の深さと同
一とされ、かつこの外輪軌道にクラウニングが施
されていることを特徴とするトランスミツシヨン
の軸受装置。 In a transmission bearing device in which the outer ring raceway of a roller bearing is directly provided on the inner diameter of the gear boss, and the gear and outer ring raceway are each blanched to a suitable depth, the outer ring raceway on the inner diameter of the gear boss is desiccated. A bearing device for a transmission, characterized in that the depth of the charring is the same as the depth of the charring applied to the gear, and the outer ring raceway is crowned.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP1985065780U JPH0217243Y2 (en) | 1985-05-04 | 1985-05-04 |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP1985065780U JPH0217243Y2 (en) | 1985-05-04 | 1985-05-04 |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS61182454U JPS61182454U (en) | 1986-11-14 |
| JPH0217243Y2 true JPH0217243Y2 (en) | 1990-05-14 |
Family
ID=30598081
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP1985065780U Expired JPH0217243Y2 (en) | 1985-05-04 | 1985-05-04 |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPH0217243Y2 (en) |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2016121419A1 (en) * | 2015-01-28 | 2016-08-04 | Ntn株式会社 | Tapered roller bearing |
| CN107110204A (en) * | 2015-01-28 | 2017-08-29 | Ntn株式会社 | Taper roll bearing |
| CN108884864A (en) * | 2016-04-01 | 2018-11-23 | Ntn株式会社 | Tapered roller bearing |
Families Citing this family (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| GB8723032D0 (en) * | 1987-10-01 | 1987-11-04 | Timkin Co | Vehicle wheel bearing |
| JPH0620900Y2 (en) * | 1989-09-28 | 1994-06-01 | エヌティエヌ株式会社 | Roller bearings for vehicle transmissions |
Citations (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS5084732A (en) * | 1973-12-03 | 1975-07-08 |
-
1985
- 1985-05-04 JP JP1985065780U patent/JPH0217243Y2/ja not_active Expired
Patent Citations (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS5084732A (en) * | 1973-12-03 | 1975-07-08 |
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2016121419A1 (en) * | 2015-01-28 | 2016-08-04 | Ntn株式会社 | Tapered roller bearing |
| CN107110204A (en) * | 2015-01-28 | 2017-08-29 | Ntn株式会社 | Taper roll bearing |
| CN108884864A (en) * | 2016-04-01 | 2018-11-23 | Ntn株式会社 | Tapered roller bearing |
| CN108884864B (en) * | 2016-04-01 | 2020-09-01 | Ntn株式会社 | Tapered roller bearing |
Also Published As
| Publication number | Publication date |
|---|---|
| JPS61182454U (en) | 1986-11-14 |
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