JPS6316896Y2 - - Google Patents

Info

Publication number
JPS6316896Y2
JPS6316896Y2 JP1982070814U JP7081482U JPS6316896Y2 JP S6316896 Y2 JPS6316896 Y2 JP S6316896Y2 JP 1982070814 U JP1982070814 U JP 1982070814U JP 7081482 U JP7081482 U JP 7081482U JP S6316896 Y2 JPS6316896 Y2 JP S6316896Y2
Authority
JP
Japan
Prior art keywords
inner ring
flange
tapered roller
roller bearing
small
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
Application number
JP1982070814U
Other languages
Japanese (ja)
Other versions
JPS58173825U (en
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 filed Critical
Priority to JP1982070814U priority Critical patent/JPS58173825U/en
Publication of JPS58173825U publication Critical patent/JPS58173825U/en
Application granted granted Critical
Publication of JPS6316896Y2 publication Critical patent/JPS6316896Y2/ja
Granted legal-status Critical Current

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
    • 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
    • F16C33/4605—Details of interaction of cage and race, e.g. retention or centring
    • 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
    • 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
    • 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
    • F16C2240/70—Diameters; Radii

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)

Description

【考案の詳細な説明】 この考案は円すいころ軸受の改良に関する。[Detailed explanation of the idea] This invention relates to improvements in tapered roller bearings.

一般に円すいころ軸受の内輪は、丸棒を切断→
成形鍛造→旋削→熱処理→研削の順序で加工され
るが、小鍔は円すいころの端面と直接接触して円
すいころの抜けを防止する必要上、その外径寸法
を大きくしなければならず、内輪１の成形鍛造
時、第１図のＡ部に不必要な肉がつき過ぎ材料歩
留りが悪い。 Generally, the inner ring of a tapered roller bearing is made by cutting a round bar→
Processing is performed in the order of forming, forging, turning, heat treatment, and grinding, but the outer diameter of the small flange must be made large to prevent the tapered roller from coming off as it comes into direct contact with the end surface of the tapered roller. When forming and forging the inner ring 1, too much unnecessary material is deposited on the part A in FIG. 1, resulting in a poor material yield.

また第２図に示す従来の円すいころ軸受、例え
ば実公昭44−1129号においては、小鍔を廃止し
て、内輪２の円すい軌道２ａの小径側端部に続く
円すい面に周溝３を形成し、該周溝３に保持器４
の小径側の半径方向内方フランジ４ａを嵌挿した
構造とすることにより、材料歩留りを向上させて
いるが、周溝３の底３ａが前記円すい軌道と平行
に形成されているため、この底３ａと内輪２の内
周面２ｂ間の肉厚ｔが薄くなり、内輪２の強度が
弱くなる。特に内輪の内径φ50以下の軸受におい
ては、この次点は大きな問題となる。 Furthermore, in the conventional tapered roller bearing shown in Fig. 2, for example, Utility Model Publication No. 44-1129, the small flange is abolished, and a circumferential groove 3 is formed on the conical surface continuing to the small diameter side end of the conical raceway 2a of the inner ring 2. and a retainer 4 in the circumferential groove 3.
The material yield is improved by fitting the radially inner flange 4a on the small diameter side of the circumferential groove 3, but since the bottom 3a of the circumferential groove 3 is formed parallel to the conical track, The wall thickness t between 3a and the inner peripheral surface 2b of the inner ring 2 becomes thinner, and the strength of the inner ring 2 becomes weaker. This runner-up is a big problem, especially for bearings whose inner ring has an inner diameter of φ50 or less.

この考案は以上の従来の円すいころ軸受の欠点
を解決することを目的とするもので、円すい軌道
をそれぞれ有する内輪と外輪との間に複数の円す
いころを介装するとともに、該円すいころを保持
器にて円周等配位置に保持し、内輪の大径側に円
すいころの大端面案内用の大鍔を形成するととも
に、内輪の小径側の円すい軌道上に周溝を形成
し、かつ保持器の内輪側に屈曲したフランジを前
記周溝に嵌挿せしめた円すいころ軸受において、
内輪の小端面と前記周溝との間に、内輪の内周面
から内輪の円すい軌道の小径側最端部までの高と
略等しい鍔高さを有する小鍔を形成してなる円す
いころ軸受を提供するものである。 This invention aims to solve the above-mentioned drawbacks of conventional tapered roller bearings, and includes a plurality of tapered rollers interposed between an inner ring and an outer ring, each having a tapered raceway, as well as holding the tapered rollers. A large flange for guiding the large end surface of the tapered roller is formed on the large diameter side of the inner ring, and a circumferential groove is formed on the conical raceway on the small diameter side of the inner ring, and the roller is held at evenly spaced positions on the circumference. In a tapered roller bearing in which a flange bent toward the inner ring side of the container is fitted into the circumferential groove,
A tapered roller bearing in which a small flange is formed between the small end surface of the inner ring and the circumferential groove and has a flange height approximately equal to the height from the inner circumferential surface of the inner ring to the smallest diameter side end of the conical raceway of the inner ring. It provides:

実施例について説明すると、第３図および第４
図において、１０，１１はそれぞれ円すい軌道１
０ａ，１１ａを有する内輪、外輪であつて、この
内、外輪１０，１１間には複数の円すいころ１２
が介装され、さらに前記円すいころ１２は保持器
１３によつて円周等配位置に保持されている。内
輪１０の大径側外周には円すいころ１２の大端面
を案内するための大鍔１４が形成され、内輪１０
の小径側の円すい軌道１０ａ上に断面略矩形の周
溝１６が形成されている。 To explain the example, FIGS. 3 and 4
In the figure, 10 and 11 are respectively conical orbits 1
0a, 11a, and a plurality of tapered rollers 12 are arranged between the inner and outer rings 10, 11.
are interposed therebetween, and the tapered rollers 12 are held at equidistant positions on the circumference by a cage 13. A large flange 14 for guiding the large end surface of the tapered rollers 12 is formed on the outer periphery of the large diameter side of the inner ring 10.
A circumferential groove 16 having a substantially rectangular cross section is formed on the conical raceway 10a on the smaller diameter side.

また内輪１０の小端面と周溝１６との間に、内
輪１０の内周面１０ｂから内輪１０の円すい軌道
１０ａの小径側最端部Ｂまでの高さｈと略等しい
鍔高さh1を有する小鍔１５が形成され、かつ内輪
１０の内周面１０ｂと前記周溝１６の底１６ａと
の間の肉厚t1ができるだけ厚くされている。 Further, between the small end surface of the inner ring 10 and the circumferential groove 16, a flange height h 1 is provided which is approximately equal to the height h from the inner circumferential surface 10b of the inner ring 10 to the small diameter side extreme end B of the conical raceway 10a of the inner ring 10. A small flange 15 is formed, and the wall thickness t1 between the inner circumferential surface 10b of the inner ring 10 and the bottom 16a of the circumferential groove 16 is made as thick as possible.

ここで小鍔１５の鍔高さh1が、内輪１０の内周
面１０ｂから円すい軌道１０ａの小径側最端部Ｂ
までの距離ｈと略等しいという意味は全く等しい
場合と、h1がｈよりわずかに大きいか小さい場合
をも含んでいるものである。 Here, the flange height h 1 of the small flange 15 is from the inner circumferential surface 10b of the inner ring 10 to the small diameter side most end B of the conical raceway 10a.
The meaning of "substantially equal to the distance h" includes the case where the distance h1 is completely equal to the distance h1, and the case where h1 is slightly larger or smaller than h.

さらに前記周溝１６の底１６ａは軸受の軸線０
−０に平行な略円筒面に形成されており、周溝１
６の底１６ａと内輪１０の内周面１０ｂとの間の
肉厚t1は、第５図にて明らかな如く、第２図の従
来の周溝３を設けた時の半径方向厚みｔよりもt2
だけ厚くすることができる。 Furthermore, the bottom 16a of the circumferential groove 16 is aligned with the axis 0 of the bearing.
-0 is formed on a substantially cylindrical surface parallel to the circumferential groove 1.
As is clear from FIG. 5, the wall thickness t 1 between the bottom 16a of the inner ring 10 and the inner circumferential surface 10b of the inner ring 10 is greater than the radial thickness t when the conventional circumferential groove 3 shown in FIG. 2 is provided. Also t 2
It can only be made thicker.

また１３ａは保持器１３の内輪１０側に屈曲さ
せたフランジで、その先端部１３ｂの内径は内輪
１０の小鍔１５の外周面１５ａの直径よりも小さ
くされて、周溝１６内に嵌挿され、円すいころ１
２、保持器１３と内輪１０とを分離しないように
している。 Further, 13a is a flange bent toward the inner ring 10 of the retainer 13, and the inner diameter of its tip 13b is smaller than the diameter of the outer circumferential surface 15a of the small flange 15 of the inner ring 10, and is inserted into the circumferential groove 16. , tapered roller 1
2. The retainer 13 and the inner ring 10 are not separated.

次に、第６図は別の実施例で、周溝１６の底
を、軸受の軸線０−０に平行な略円筒面に形成す
るかわりに、第２図の従来の周溝３と同様に円す
い軌道１０ａと平行な底１６ｂに形成したもので
あるが、この底１６ｂの形状としても、小鍔１５
を設けているがために、半径方向厚みt1は第２図
の従来軸受の内輪２の半径方向厚みｔよりもt3だ
け厚くなる。 Next, FIG. 6 shows another embodiment, in which the bottom of the circumferential groove 16 is formed into a substantially cylindrical surface parallel to the axis 0-0 of the bearing, but similar to the conventional circumferential groove 3 shown in FIG. Although it is formed on the bottom 16b parallel to the conical orbit 10a, the shape of the bottom 16b is similar to that of the small tsuba 15.
Therefore, the radial thickness t 1 is thicker by t 3 than the radial thickness t of the inner ring 2 of the conventional bearing shown in FIG.

さらに第７図は別の実施例であり、周溝を断面
円形の溝１７より形成し、該断面円形の周溝１７
に保持器１３のフランジ１３ａの先端部１３ｂを
嵌挿させたものである。 Furthermore, FIG. 7 shows another embodiment in which the circumferential groove is formed by a groove 17 having a circular cross section, and the circumferential groove 17 having a circular cross section.
The tip 13b of the flange 13a of the retainer 13 is inserted into the holder 13.

また第３図乃至第７図の実施例においては、小
鍔１５の外周面１５ａは軸受の軸線０−０に平行
な円筒面に形成されているが、第８図の実施例の
如く小鍔１５の外周面１５ａの内輪小端面側に該
小端面に向つて次第に直径が減少する傾斜面１８
を形成してもよく、さらに第９図の実施例の如
く、小鍔１５を断面円弧に形成してもよい。 Further, in the embodiments shown in FIGS. 3 to 7, the outer peripheral surface 15a of the small flange 15 is formed into a cylindrical surface parallel to the axis 0-0 of the bearing, but as in the embodiment shown in FIG. An inclined surface 18 whose diameter gradually decreases toward the inner ring small end surface of the outer circumferential surface 15a of No. 15.
Furthermore, as in the embodiment shown in FIG. 9, the small flange 15 may be formed to have an arcuate cross section.

第８図および第９図の実施例の小鍔１５形状と
することにより、保持器１３のフランジ１３ａの
周溝１６内への組込みが容易となる。 By forming the small flange 15 in the embodiment shown in FIGS. 8 and 9, the flange 13a of the retainer 13 can be easily assembled into the circumferential groove 16.

さらに保持器１３は弾性を利用して周溝１６，
１７内に嵌挿させる関係上、好ましくは第１０図
に示すように合成樹脂より形成するのがよい。 Furthermore, the retainer 13 utilizes elasticity to provide a circumferential groove 16,
17, it is preferably made of synthetic resin as shown in FIG.

さらにまた保持器１３のフランジ１３ａの先端
部１３ｂは、円周上に連続させてもよいが、特に
弾性を付与したい場合には、第１１図の如く、フ
ランジ１３ａの内周先端部１３ｂを円周上、適当
な数、適当な形状に切り欠いで不連続にしてもよ
い。 Furthermore, the distal end 13b of the flange 13a of the retainer 13 may be continuous on the circumference, but if it is particularly desired to impart elasticity, the inner distal end 13b of the flange 13a may be made circular as shown in FIG. It may be made discontinuous by cutting out an appropriate number and shape on the circumference.

この考案は以上の構成よりなり、内輪の小鍔の
鍔高さｈを、内輪内周面から内輪の円すい軌道の
小径側最端部までの高さh1に略等しくしたため、
内輪の成形鍛造時の歩留りがよくなるとともに、
周溝の底と内輪内周面との間の肉厚t1を厚くする
ことができるため内輪の強度が向上する。特に第
３図および第４図の実施例においては、周溝の底
が軸受の軸線０−０に平行な略円筒面であるた
め、肉厚t1を特に厚くすることができる。 This invention has the above structure, and the height h of the small flange of the inner ring is made approximately equal to the height h 1 from the inner peripheral surface of the inner ring to the end of the small diameter side of the conical raceway of the inner ring.
In addition to improving the yield when forming and forging the inner ring,
Since the wall thickness t1 between the bottom of the circumferential groove and the inner circumferential surface of the inner ring can be increased, the strength of the inner ring is improved. Particularly in the embodiments shown in FIGS. 3 and 4, since the bottom of the circumferential groove is a substantially cylindrical surface parallel to the bearing axis 0-0, the wall thickness t1 can be particularly thick.

特に内輪の内径φ50以下の軸受における強度上
の問題は解消することができる。 In particular, strength problems in bearings with inner rings with inner diameters of φ50 or less can be resolved.

【図面の簡単な説明】[Brief explanation of drawings]

第１図は従来の成形鍛造時の内輪の縦断面図、
第２図はさらに別の従来の円すいころ軸受の縦断
面図、第３図はこの考案の実施例の縦断面図、第
４図は第３図の要部拡大図、第５図は第２図の周
溝と第３図の周溝との比較図、第６図、第７図、
第８図および第９図はそれぞれ別の実施例の要部
拡大図、第１０図は保持器の別の実施例の断面
図、第１１図はさらに保持器の別の実施例の一部
側面図である。 １０……内輪、１１……外輪、１２……円すい
ころ、１３……保持器、１３ａ……フランジ、１
４……大鍔、１５……小鍔、１６，１７……周
溝、Ｂ……円すい軌道端部。 Figure 1 is a vertical cross-sectional view of the inner ring during conventional forming forging.
Fig. 2 is a longitudinal sectional view of yet another conventional tapered roller bearing, Fig. 3 is a longitudinal sectional view of an embodiment of this invention, Fig. 4 is an enlarged view of the main part of Fig. 3, and Fig. 5 is a longitudinal sectional view of another conventional tapered roller bearing. A comparison diagram of the circumferential groove shown in the figure and the circumferential groove shown in Fig. 3, Fig. 6, Fig. 7,
8 and 9 are enlarged views of main parts of different embodiments, FIG. 10 is a sectional view of another embodiment of the cage, and FIG. 11 is a partial side view of another embodiment of the cage. It is a diagram. 10... Inner ring, 11... Outer ring, 12... Tapered roller, 13... Cage, 13a... Flange, 1
4...Large tsuba, 15...Small tsuba, 16, 17...Peripheral groove, B...Conical raceway end.

Claims (1)

【実用新案登録請求の範囲】 (1) 円すい軌道をそれぞれ有する内輪と外輪との
間に複数の円すいころを介装するとともに、該
円すいころを保持器にて円周等配位置に保持
し、内輪の大径側に円すいころの大端面案内用
の大鍔を形成するとともに、内輪の小径側の円
すい軌道上に周溝を形成し、かつ保持器の内輪
側に屈曲したフランジを前記周溝に嵌挿せしめ
た円すいころ軸受において、内輪の小端面と前
記周溝との間に、内輪の内周面から内輪の円す
い軌道の小径側最端部までの高さと略等しい鍔
高さを有する小鍔を形成してなる円すいころ軸
受。 (2) 前記周溝が断面略矩形からなる実用新案登録
請求の範囲(1)に記載の円すいころ軸受。 (3) 前記周溝が断面円形からなる実用新案登録請
求の範囲(1)に記載の円すいころ軸受。 (4) 前記小鍔の外周面が軸受の軸線に平行である
実用新案登録請求の範囲(1)または(2)に記載の円
すいころ軸受。 (5) 前記小鍔の外周面の内輪小端面側に、該小端
面に向つて次第に直径が減少する傾斜面を形成
してなる実用新案登録請求の範囲(4)に記載の円
すいころ軸受。 (6) 前記小鍔の外周面が断面円弧からなる実用新
案登録請求の範囲(1)または(2)に記載の円すいこ
ろ軸受。 (7) 前記保持器が合成樹脂よりなる実用新案登録
請求の範囲(1)から(6)のうちのいずれか１つに記
載の円すいころ軸受。 (8) 前記保持器のフランジの内周先端部が円周上
不連続である実用新案登録請求の範囲(1)から(7)
のうちのいずれか１つに記載の円すいころ軸
受。[Scope of Claim for Utility Model Registration] (1) A plurality of tapered rollers are interposed between an inner ring and an outer ring each having a tapered raceway, and the tapered rollers are held at equidistant positions on the circumference by a cage, A large flange for guiding the large end surface of the tapered rollers is formed on the large diameter side of the inner ring, a circumferential groove is formed on the conical raceway on the small diameter side of the inner ring, and a bent flange is formed on the inner ring side of the cage in the circumferential groove. In the tapered roller bearing fitted into the bearing, there is a flange height between the small end surface of the inner ring and the circumferential groove that is approximately equal to the height from the inner circumferential surface of the inner ring to the end of the conical raceway on the small diameter side of the inner ring. A tapered roller bearing with a small flange. (2) The tapered roller bearing according to claim (1), wherein the circumferential groove has a substantially rectangular cross section. (3) The tapered roller bearing according to claim (1), wherein the circumferential groove has a circular cross section. (4) The tapered roller bearing according to claim (1) or (2), wherein the outer peripheral surface of the small flange is parallel to the axis of the bearing. (5) The tapered roller bearing according to claim (4), which is a registered utility model, wherein an inclined surface whose diameter gradually decreases toward the small end surface is formed on the inner ring small end surface side of the outer peripheral surface of the small flange. (6) The tapered roller bearing according to claim (1) or (2), wherein the outer peripheral surface of the small flange has a circular arc cross section. (7) The tapered roller bearing according to any one of claims (1) to (6), wherein the cage is made of synthetic resin. (8) Utility model registration claims (1) to (7) in which the inner peripheral tip of the flange of the retainer is discontinuous on the circumference.
A tapered roller bearing according to any one of the above.
JP1982070814U 1982-05-15 1982-05-15 tapered roller bearing Granted JPS58173825U (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
JP1982070814U JPS58173825U (en) 1982-05-15 1982-05-15 tapered roller bearing

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
JP1982070814U JPS58173825U (en) 1982-05-15 1982-05-15 tapered roller bearing

Publications (2)

Publication Number Publication Date
JPS58173825U JPS58173825U (en) 1983-11-21
JPS6316896Y2 true JPS6316896Y2 (en) 1988-05-13

Family

ID=30080458

Family Applications (1)

Application Number Title Priority Date Filing Date
JP1982070814U Granted JPS58173825U (en) 1982-05-15 1982-05-15 tapered roller bearing

Country Status (1)

Country Link
JP (1) JPS58173825U (en)

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR3000772B1 (en) * 2013-01-10 2015-06-19 Ntn Snr Roulements CAGE FOR BEARING UNIT, AND BEARING UNIT EQUIPPED WITH SUCH A CAGE.
JP6694288B2 (en) * 2016-02-05 2020-05-13 ナブテスコ株式会社 Roller bearing
JP2017180481A (en) * 2016-03-28 2017-10-05 Ntn株式会社 Conical roller bearing
WO2019054466A1 (en) * 2017-09-14 2019-03-21 Ntn株式会社 Tapered roller bearing

Also Published As

Publication number Publication date
JPS58173825U (en) 1983-11-21

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