JPH09236131A - Roller bearing - Google Patents
Roller bearingInfo
- Publication number
- JPH09236131A JPH09236131A JP8071218A JP7121896A JPH09236131A JP H09236131 A JPH09236131 A JP H09236131A JP 8071218 A JP8071218 A JP 8071218A JP 7121896 A JP7121896 A JP 7121896A JP H09236131 A JPH09236131 A JP H09236131A
- Authority
- JP
- Japan
- Prior art keywords
- roller
- inner ring
- collar
- diameter
- end surface
- 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
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
- F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
- F16C33/30—Parts of ball or roller bearings
- F16C33/34—Rollers; Needles
- F16C33/36—Rollers; Needles with bearing-surfaces other than cylindrical, e.g. tapered; with grooves in the bearing surfaces
-
- 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
- F16C19/225—Details of the ribs supporting the end of 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
- F16C19/24—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 radial load mainly
- F16C19/26—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 radial load mainly with a single row of 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
- F16C19/36—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
-
- 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
- F16C2326/00—Articles relating to transporting
- F16C2326/10—Railway vehicles
Abstract
Description
【０００１】[0001]
【発明の属する技術分野】この発明は、工作機械主軸用
軸受、鉄道車両車軸用軸受など、低発熱を必要する軸受
に応用される円すいころ軸受や円筒ころ軸受等のころ軸
受に関する。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a roller bearing such as a tapered roller bearing or a cylindrical roller bearing, which is applied to bearings that require low heat generation such as bearings for machine tool spindles and bearings for railroad vehicles.
【０００２】[0002]
【従来の技術と発明が解決しようとする課題】円すいこ
ろ軸受では、図４に示すように、アキシャル荷重を受け
るころ５１の外径面と、ころ端面が内輪大鍔５２に接す
る接触部Ｐとがころ中心Ｏに対して同一半径上に位置し
ないため、接触部Ｐで滑りが発生する。そのため、高速
回転時の発熱が大となる。例えば、工作機械主軸用ころ
軸受の発熱は、主軸の熱膨張を生じさせ、これが工作物
の精度の誤差を生じる原因となる。また、鉄道車両用車
軸軸受では、その軸受の発熱は、グリースの軟化、油化
を生じ、シール部からのグリース洩れ、油分洩れを生じ
る原因となる。2. Description of the Related Art In a tapered roller bearing, as shown in FIG. 4, an outer diameter surface of a roller 51 that receives an axial load and a contact portion P where the roller end surface contacts the inner ring large collar 52. Is not located on the same radius with respect to the center O of the roller, so that slip occurs at the contact portion P. Therefore, heat generation during high-speed rotation becomes large. For example, heat generation of a roller bearing for a machine tool spindle causes thermal expansion of the spindle, which causes an error in accuracy of a workpiece. Further, in an axle bearing for a railroad vehicle, heat generation of the bearing causes softening and oiling of grease, which causes grease leakage and oil leakage from the seal portion.
【０００３】この発明は、上記の課題を解消するもので
あり、ころと内輪鍔との滑りによる発熱を低減すること
によって高速回転に耐え得るようにしたころ軸受を提供
することを目的とする。SUMMARY OF THE INVENTION The present invention solves the above problems, and an object of the present invention is to provide a roller bearing capable of withstanding high speed rotation by reducing heat generation due to sliding between the roller and the inner ring collar.
【０００４】[0004]
【課題を解決するための手段】この発明のころ軸受は、
ころ端面の内輪鍔と接触する径方向位置を、ころ外径面
の内輪転接部分の延長面となる円すい面または円筒面が
ころ端面と交わる位置としたものである。このような接
触位置にすることを可能とするため、ころの端部外周に
鍔状部を設け、内輪鍔と接触するころ端面の直径を、こ
ろの外径面における内輪転接部分の最大直径よりも大き
くする。円すいころ軸受の場合は、円すいころの大径端
に前記鍔状部を設ける。また、これらの構成において、
前記ころの鍔状部は、前記転接部分からころ端面側へ円
すい状に拡径するものとしても良く、また円柱状とし、
あるいは断面円弧状としても良い。この構成によると、
軸受回転時において、ころは内外輪との転接に伴って回
転するが、ころ端面の内輪鍔と接触する径方向位置が、
ころ外径面の延長面となる円すい面または円筒面と交わ
る位置となっているため、ころ端面と内輪鍔との接触部
における周速差が小さく、周速差による滑りが少なくな
る。このため、滑りによる発熱が抑制される。円すいこ
ろ軸受の場合は、内輪が両鍔の場合でも、アキシャル荷
重によって内輪大鍔ところ大径端との接触圧が強くなる
が、この内輪大鍔側で、前記のようにころ端面の内輪鍔
と接触する径方向位置をころ外径面の延長面に交わる位
置とすることで、滑りによる発熱が抑制される。The roller bearing according to the present invention comprises:
The radial position of the roller end surface in contact with the inner ring flange is the position where the conical surface or the cylindrical surface, which is the extension surface of the inner ring rolling contact portion of the roller outer diameter surface, intersects with the roller end surface. In order to enable such contact position, a collar-shaped part is provided on the outer circumference of the end of the roller, and the diameter of the roller end surface that contacts the inner ring collar is the maximum diameter of the inner ring rolling contact part on the outer diameter surface of the roller. Bigger than. In the case of a tapered roller bearing, the flange portion is provided on the large diameter end of the tapered roller. Also, in these configurations,
The brim-shaped portion of the roller may be one in which the diameter increases in a cone shape from the rolling contact portion to the roller end surface side, and has a cylindrical shape,
Alternatively, the cross section may be arcuate. According to this configuration,
At the time of bearing rotation, the roller rotates with rolling contact with the inner and outer rings, but the radial position of the roller end surface in contact with the inner ring collar is
Since it is located at a position where it intersects with a conical surface or a cylindrical surface that is an extension surface of the roller outer diameter surface, the peripheral speed difference at the contact portion between the roller end surface and the inner ring flange is small, and slippage due to the peripheral speed difference is reduced. Therefore, heat generation due to slippage is suppressed. In the case of a tapered roller bearing, even if the inner ring has both flanges, the contact pressure with the large diameter end of the inner ring becomes larger due to the axial load. By making the radial position in contact with the extended position of the roller outer diameter surface, heat generation due to slippage is suppressed.
【０００５】[0005]
【発明の実施の形態】この発明の一実施形態を図１に基
づいて説明する。この例は円すいころ軸受に適用したも
のである。両鍔付きの内輪１と鍔無しの外輪２との間
に、保持器３に保持された円すいころ４が介在させてあ
る。DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS One embodiment of the present invention will be described with reference to FIG. This example is applied to a tapered roller bearing. A tapered roller 4 held by a cage 3 is interposed between an inner ring 1 with both collars and an outer ring 2 without a collar.
【０００６】ころ４は、大径端の外周に鍔状部５を設
け、内輪大鍔１ａと接触するころ端面４ａの直径ｄ１
を、ころ４の外径面４ｂにおける内輪転接部分４ｂａの
最大直径ｄ２よりも大きくしてある。これにより、ころ
端面４ａの内輪大鍔１ａと接触する径方向位置Ｑを、こ
ろ外径面４ｂの内輪転接部分４ｂａの延長面となる円す
い面Ｓがころ端面４ａと交わる位置としてある。このよ
うな接触が行われるように、内輪大鍔１ａの内側面の形
状も、ころ端面１ａとの接触部が膨らむ断面形状として
ある。ころ４の鍔状部５は、内輪転接部分４ｂａからこ
ろ端面４ａ側へ円すい状に拡径する形状としてある。こ
ろ端面４ａは、全体を軸心部が若干突出する球面状の凸
曲面とし、かつ周縁部を円弧状断面の面取状に形成して
ある。内輪１の軌道面１ｃの両端には、内輪小鍔１ｂ側
に研摩盗み６を設け、内輪大鍔１ａ側に、ころ４の鍔状
部５が嵌まる研摩盗み兼用の周溝７が形成してある。周
溝７は、底部を丸くしたＶ溝状とし、かつ内輪大鍔１ａ
側の溝内側面を、内輪大鍔１ａの内側面よりも若干凹む
曲面に形成してある。外輪２は、ころ４の鍔状部５が干
渉しないように、内輪１よりも幅を狭めてある。The roller 4 is provided with a collar-shaped portion 5 on the outer periphery of the large-diameter end, and the diameter d1 of the roller end surface 4a in contact with the inner-ring large collar 1a.
Is larger than the maximum diameter d2 of the inner ring rolling contact portion 4ba on the outer diameter surface 4b of the roller 4. As a result, the radial position Q of the roller end surface 4a in contact with the inner ring large flange 1a is the position where the conical surface S, which is an extension surface of the inner ring rolling contact portion 4ba of the roller outer diameter surface 4b, intersects with the roller end surface 4a. In order to make such contact, the shape of the inner side surface of the inner ring large flange 1a is also a cross-sectional shape in which the contact portion with the roller end surface 1a swells. The collar-shaped portion 5 of the roller 4 is shaped so as to expand in a conical shape from the inner ring rolling contact portion 4ba to the roller end surface 4a side. The roller end surface 4a is formed as a spherical convex curved surface with its shaft portion slightly protruding, and its peripheral portion is formed in a chamfered shape having an arc-shaped cross section. At both ends of the raceway surface 1c of the inner ring 1, there are provided abrasive grooves 6 on the side of the inner ring small flange 1b, and on the side of the inner ring large flange 1a, there are formed circumferential grooves 7 also serving as the abrasive grooves for fitting the collar-shaped portions 5 of the rollers 4. There is. The circumferential groove 7 has a V-shaped groove with a rounded bottom, and the inner ring large flange 1a.
The inner side surface of the side groove is formed into a curved surface slightly recessed from the inner side surface of the inner ring large flange 1a. The outer ring 2 is narrower in width than the inner ring 1 so that the collar-shaped portion 5 of the roller 4 does not interfere.
【０００７】この構成によると、軸受回転時において、
ころ４は内外輪１，２との転接に伴って回転するが、こ
ろ端面４ａの内輪大鍔１ａと接触する径方向位置Ｑが、
ころ外径面４ｂの延長面となる円すい面Ｓと交わる位置
となっているため、ころ端面４ａと内輪大鍔５との接触
部の周速差が小さく、周速差による滑りが少なくなる。
このように、高速回転時の円すいころ軸受の発熱主要因
であるころ４と内輪大鍔１ａとの滑りが少なくたるた
め、発熱の飛躍的な低減が期待できる。According to this structure, when the bearing is rotating,
The roller 4 rotates with rolling contact with the inner and outer rings 1, 2, but the radial position Q of the roller end surface 4a in contact with the inner ring large collar 1a is
Since it is located at a position where it intersects with the conical surface S that is an extension of the roller outer diameter surface 4b, the peripheral speed difference between the contact portion between the roller end surface 4a and the inner ring large collar 5 is small, and slippage due to the peripheral speed difference is reduced.
As described above, since the slippage between the roller 4 and the inner ring large collar 1a, which is the main cause of heat generation of the tapered roller bearing during high-speed rotation, is reduced, a dramatic reduction in heat generation can be expected.
【０００８】また、この実施形態では、ころ４の鍔状部
５の形状を、ころ外径面４ｂの内輪転接部分４ｂａから
ころ端面４ａ側へ円すい状に拡径する形状としてあるた
め、ころ４の鍔状部５との接触回避用に内輪１に形成さ
れる周溝７が小さな断面のものですみ、かつ内輪大鍔１
ａの内面が内径側へ広がることになる。そのため、鍔状
部５の突出高さが低くても、ころ端面４ａの内輪大鍔１
ａと接触する径方向位置Ｑを、ころ外径面４ｂの延長面
Ｓ上に位置させることが容易となる。特に、円すいころ
軸受の場合、内輪１の軌道面１ｃが円すい面であるた
め、前記のように鍔状部５を小さくできる効果が得易
い。Further, in this embodiment, since the collar-shaped portion 5 of the roller 4 is shaped so as to expand in a conical shape from the inner ring rolling contact portion 4ba of the roller outer diameter surface 4b to the roller end surface 4a side, The peripheral groove 7 formed in the inner ring 1 for avoiding contact with the collar-shaped portion 5 of 4 has a small cross section, and the inner ring large collar 1
The inner surface of “a” expands toward the inner diameter side. Therefore, even if the protrusion height of the collar-shaped portion 5 is low, the inner ring large collar 1 of the roller end surface 4a is
It becomes easy to position the radial position Q in contact with a on the extension surface S of the roller outer diameter surface 4b. Particularly, in the case of a tapered roller bearing, since the raceway surface 1c of the inner ring 1 is a tapered surface, it is easy to obtain the effect of making the collar-shaped portion 5 small as described above.
【０００９】なお、前記実施形態ではころ４の鍔状部５
の形状を円すい状としたが、鍔状部５の形状は種々の形
状とできる。例えば、図２（Ａ）のように、鍔状部５を
円筒状としても良い。このように鍔状部５を円筒状とす
ることで、鍔状部５を堅固なものとでき、耐久性が向上
する。図２（Ｂ）の例は、ころ４の鍔状部５の形状を、
円すい状であって、かつ若干凹曲面となるように丸みを
持たせた形状としてある。図２（Ｃ）の例は、ころ４の
鍔状部５の形状を、断面が半円の円弧状となる形状とし
てある。これに伴い、内輪１の円周溝７の断面形状を円
弧状としてある。このように、ころ４の鍔状部５を円弧
状とした場合、鍔状部５の加工が容易であり、かつ内輪
１の円周溝７を前記のように円弧状とできて、加工が容
易となる。In the above embodiment, the collar-shaped portion 5 of the roller 4 is used.
Although the shape of 1 is a cone shape, the shape of the collar-shaped portion 5 can be various shapes. For example, as shown in FIG. 2A, the collar-shaped portion 5 may have a cylindrical shape. By forming the collar-shaped portion 5 into a cylindrical shape in this manner, the collar-shaped portion 5 can be made solid and the durability is improved. In the example of FIG. 2B, the shape of the collar-shaped portion 5 of the roller 4 is
It has a conical shape and is rounded to have a slightly concave curved surface. In the example of FIG. 2 (C), the brim-shaped portion 5 of the roller 4 has a semicircular arc-shaped cross section. Along with this, the cross-sectional shape of the circumferential groove 7 of the inner ring 1 is arcuate. As described above, when the collar-shaped portion 5 of the roller 4 is formed in an arc shape, the collar-shaped portion 5 can be easily processed, and the circumferential groove 7 of the inner ring 1 can be formed in the arc shape as described above. It will be easy.
【００１０】図３はこの発明の他の実施形態を示す。こ
の例は、円筒ころ軸受に適用したものである。内輪１１
は両鍔付きとし、外輪１２は、片方の鍔部を分割して側
輪１２ａとしてある。これら内輪１１と外輪１２の間
に、保持器１３に保持された円筒ころ１４を介在させて
ある。この例では、ころ１４の両端部の外周に鍔状部１
５を設け、両側の内輪鍔１１ａ，１１ａと接触するころ
端面１４ａの直径を、ころ１４の外径面における内輪転
接部分の直径よりも大きくしてある。また、ころ端面１
４ａの内輪鍔１１ａと接触する径方向位置Ｑ′を、ころ
外径面の延長面となる円筒面Ｓ′がころ端面１４ａと交
わる位置としてある。この構成の場合も、ころ端面１４
ａと内輪鍔１１ａとの滑りを少なくして発熱を低減させ
ることができる。FIG. 3 shows another embodiment of the present invention. This example is applied to a cylindrical roller bearing. Inner ring 11
Has two collars, and the outer ring 12 has a side ring 12a obtained by dividing one of the collars. A cylindrical roller 14 held by a cage 13 is interposed between the inner ring 11 and the outer ring 12. In this example, the collar-shaped portion 1 is formed on the outer circumference of both ends of the roller 14.
5, the diameter of the roller end surface 14a that contacts the inner ring flanges 11a, 11a on both sides is made larger than the diameter of the inner ring rolling contact portion on the outer diameter surface of the roller 14. Also, the roller end surface 1
The radial position Q'that contacts the inner ring collar 11a of 4a is the position where the cylindrical surface S'which is an extension of the roller outer diameter surface intersects the roller end surface 14a. Also in this configuration, the roller end surface 14
It is possible to reduce the heat generation by reducing the slip between the a and the inner ring collar 11a.
【００１１】[0011]
【発明の効果】この発明のころ軸受は、ころ端面の内輪
鍔と接触する径方向位置を、ころ外径面の内輪転接部分
の延長面となる円すい面または円筒面がころ端面と交わ
る位置としたため、高速回転時のころ軸受の発熱主要因
であるころと内輪鍔との滑りを少なくすることができ、
これによって低発熱化が期待できる。特に、円すいころ
軸受の場合に、発熱主要因である内輪大鍔ところとの滑
りを少なくでき、これによって飛躍的な低発熱化が期待
できる。According to the roller bearing of the present invention, the radial position of the roller end surface in contact with the inner ring flange is the position where the conical surface or the cylindrical surface, which is the extension surface of the inner ring rolling contact portion of the roller outer diameter surface, intersects with the roller end surface. Therefore, it is possible to reduce the slip between the roller and the inner ring flange, which is the main cause of heat generation of the roller bearing during high-speed rotation.
This can be expected to reduce heat generation. In particular, in the case of a tapered roller bearing, it is possible to reduce the slippage with the large inner ring of the inner ring, which is the main cause of heat generation, and this can be expected to dramatically reduce heat generation.
【図１】この発明の一実施形態の断面図である。FIG. 1 is a sectional view of an embodiment of the present invention.
【図２】図１の鎖線IIで囲む部分の各種変形例を示す断
面図である。FIG. 2 is a cross-sectional view showing various modifications of a portion surrounded by a chain line II in FIG.
【図３】この発明の他の実施形態の断面図である。FIG. 3 is a cross-sectional view of another embodiment of the present invention.
【図４】従来例の断面図である。FIG. 4 is a sectional view of a conventional example.
１…内輪、１ａ…内輪大鍔、２…外輪、４…円すいこ
ろ、４ａ…ころ端面、４ｂ…外径面、４ｂａ…転接面部
分、５…鍔状部、７…周溝、１１…内輪、１２…外輪、
１４…円筒ころ、１５…鍔状部、Ｓ，Ｓ′…円すい面、
Ｑ，Ｑ′…径方向位置DESCRIPTION OF SYMBOLS 1 ... Inner ring, 1a ... Inner ring large collar, 2 ... Outer ring, 4 ... Tapered roller, 4a ... Roller end surface, 4b ... Outer diameter surface, 4ba ... Rolling contact surface portion, 5 ... Collar portion, 7 ... Circumferential groove, 11 ... Inner ring, 12 ... Outer ring,
14 ... Cylindrical roller, 15 ... Collar-like part, S, S '... Conical surface,
Q, Q '... Radial position
Claims (5)
と接触するころ端面の直径を、ころの外径面における内
輪転接部分の最大直径よりも大きくし、ころ端面の内輪
鍔と接触する径方向位置を、前記ころ外径面の内輪転接
部分の延長面となる円すい面または円筒面がころ端面と
交わる位置としたころ軸受。Claim: What is claimed is: 1. A roller is provided with a collar-shaped portion on the outer circumference of the end portion of the roller, and the diameter of the roller end surface that comes into contact with the inner ring collar is made larger than the maximum diameter of the inner ring rolling contact portion on the outer diameter surface of the roller. A roller bearing in which a radial position in contact with the flange is set to a position where a conical surface or a cylindrical surface, which is an extension surface of the inner ring rolling contact portion of the roller outer diameter surface, intersects with the roller end surface.
すいころの大径端に前記鍔状部を設けた請求項１記載の
ころ軸受。2. The roller bearing according to claim 1, wherein the roller is a tapered roller, and the flanged portion is provided at a large diameter end of the tapered roller.
ころ端面側へ円すい状に拡径する形状とした請求項１ま
たは請求項２記載のころ軸受。3. The roller bearing according to claim 1, wherein the collar-shaped portion of the roller has a shape in which the diameter of the roller is increased from the inner ring rolling contact portion toward the roller end surface side in a conical shape.
１または請求項２記載のころ軸受。4. The roller bearing according to claim 1, wherein the collar-shaped portion of the roller is cylindrical.
求項１または請求項２記載のころ軸受。5. The roller bearing according to claim 1, wherein the collar-shaped portion of the roller has an arcuate cross section.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP8071218A JPH09236131A (en) | 1996-02-29 | 1996-02-29 | Roller bearing |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP8071218A JPH09236131A (en) | 1996-02-29 | 1996-02-29 | Roller bearing |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JPH09236131A true JPH09236131A (en) | 1997-09-09 |
Family
ID=13454328
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP8071218A Pending JPH09236131A (en) | 1996-02-29 | 1996-02-29 | Roller bearing |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPH09236131A (en) |
Cited By (10)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH11190333A (en) * | 1997-09-22 | 1999-07-13 | Nippon Seiko Kk | Conical roller bearing |
| US6464398B2 (en) | 2000-05-22 | 2002-10-15 | Nsk Ltd. | Roller bearing |
| US6767134B2 (en) | 2001-07-05 | 2004-07-27 | Nsk Ltd. | Roller bearing |
| DE10262085B4 (en) * | 2001-07-05 | 2006-02-16 | Nsk Ltd. | Roller bearing e.g. conical roller bearing, has contact portion, of end face of each roller to be contacted with collar portion, which is ground so as to have continuously curved shape |
| JP2007218292A (en) * | 2006-02-14 | 2007-08-30 | Ntn Corp | Bearing apparatus for wheel |
| US7416346B2 (en) | 2003-06-12 | 2008-08-26 | Nsk Ltd. | Cylindrical roller bearing |
| WO2009063802A1 (en) * | 2007-11-12 | 2009-05-22 | Ntn Corporation | Tapered roller bearing |
| JP2009121513A (en) * | 2007-11-12 | 2009-06-04 | Ntn Corp | Tapered roller bearing |
| JP2015218748A (en) * | 2014-05-14 | 2015-12-07 | Ntn株式会社 | Thrust conical roller bearing |
| DE102006019984B4 (en) * | 2006-04-29 | 2017-10-26 | Schaeffler Technologies AG & Co. KG | radial bearings |
-
1996
- 1996-02-29 JP JP8071218A patent/JPH09236131A/en active Pending
Cited By (14)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH11190333A (en) * | 1997-09-22 | 1999-07-13 | Nippon Seiko Kk | Conical roller bearing |
| US6464398B2 (en) | 2000-05-22 | 2002-10-15 | Nsk Ltd. | Roller bearing |
| DE10230357C5 (en) | 2001-07-05 | 2019-05-29 | Nsk Ltd. | Rolling |
| US6767134B2 (en) | 2001-07-05 | 2004-07-27 | Nsk Ltd. | Roller bearing |
| DE10262085B4 (en) * | 2001-07-05 | 2006-02-16 | Nsk Ltd. | Roller bearing e.g. conical roller bearing, has contact portion, of end face of each roller to be contacted with collar portion, which is ground so as to have continuously curved shape |
| DE10230357B4 (en) * | 2001-07-05 | 2006-10-05 | Nsk Ltd. | roller bearing |
| USRE48586E1 (en) | 2001-07-05 | 2021-06-08 | Nsk Ltd. | Roller bearing |
| US7416346B2 (en) | 2003-06-12 | 2008-08-26 | Nsk Ltd. | Cylindrical roller bearing |
| JP2007218292A (en) * | 2006-02-14 | 2007-08-30 | Ntn Corp | Bearing apparatus for wheel |
| DE102006019984B4 (en) * | 2006-04-29 | 2017-10-26 | Schaeffler Technologies AG & Co. KG | radial bearings |
| JP2009121513A (en) * | 2007-11-12 | 2009-06-04 | Ntn Corp | Tapered roller bearing |
| US8596877B2 (en) | 2007-11-12 | 2013-12-03 | Ntn Corporation | Tapered roller bearing |
| WO2009063802A1 (en) * | 2007-11-12 | 2009-05-22 | Ntn Corporation | Tapered roller bearing |
| JP2015218748A (en) * | 2014-05-14 | 2015-12-07 | Ntn株式会社 | Thrust conical roller bearing |
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