JPH1089353A - Tapered roller bearing - Google Patents
Tapered roller bearingInfo
- Publication number
- JPH1089353A JPH1089353A JP24764596A JP24764596A JPH1089353A JP H1089353 A JPH1089353 A JP H1089353A JP 24764596 A JP24764596 A JP 24764596A JP 24764596 A JP24764596 A JP 24764596A JP H1089353 A JPH1089353 A JP H1089353A
- Authority
- JP
- Japan
- Prior art keywords
- gap
- diameter side
- diameter end
- bearing
- lubricating oil
- 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
- 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
- F16C33/54—Cages for rollers or needles made from wire, strips, or sheet metal
- F16C33/542—Cages for rollers or needles made from wire, strips, or sheet metal made from sheet metal
- F16C33/543—Cages for rollers or needles made from wire, strips, or sheet metal made from sheet metal from a single part
-
- 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
- F16C33/66—Special parts or details in view of lubrication
- F16C33/6637—Special parts or details in view of lubrication with liquid lubricant
- F16C33/6659—Details of supply of the liquid to the bearing, e.g. passages or nozzles
- F16C33/6674—Details of supply of the liquid to the bearing, e.g. passages or nozzles related to the amount supplied, e.g. gaps to restrict flow of the liquid
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Rolling Contact Bearings (AREA)
Abstract
Description
【０００１】[0001]
【発明の属する技術分野】この発明は、潤滑油の流れを
コントロールして軸受はくりを防止できる円すいころ軸
受に関する。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a tapered roller bearing capable of controlling the flow of a lubricating oil and preventing the bearing from breaking off.
【０００２】[0002]
【従来の技術】一般に、円すいころ軸受が使用される環
境では、オイル潤滑下で外部からの異物が侵入しやす
く、異物かみ込みによる軸受はくりが発生しやすいとい
う問題がある。2. Description of the Related Art Generally, in an environment in which a tapered roller bearing is used, there is a problem that foreign matter from the outside easily enters under oil lubrication, and the bearing is liable to be cut off by the foreign matter.
【０００３】[0003]
【発明が解決しようとする課題】そこで、この発明の目
的は、異物かみ込みによる軸受はくりを防止でき、軸受
寿命を向上できる円すいころ軸受を提供することにあ
る。SUMMARY OF THE INVENTION Accordingly, an object of the present invention is to provide a tapered roller bearing which can prevent the bearing from being peeled off by foreign matter and can extend the life of the bearing.
【０００４】[0004]
【課題を解決するための手段】本発明者らは、次の実施
の形態で詳細に説明するような潤滑油流れに関する実験
を行うことによって、円すいころ軸受の回転時の潤滑油
の流れについて次の４つのことを確認した。The present inventors conducted an experiment on the lubricating oil flow as will be described in detail in the following embodiment, and found that the lubricating oil flow during the rotation of the tapered roller bearing was as follows. The following four things were confirmed.
【０００５】 図３に示すように、回転時に、外輪の
小径側端部と保持器の小径側端部との間の第１隙間Ａか
ら潤滑油が排出される。As shown in FIG. 3, during rotation, lubricating oil is discharged from a first gap A between the small-diameter end of the outer ring and the small-diameter end of the cage.
【０００６】 また、保持器の小径側端部と内輪の小
径側端部との間の第２隙間Ｂへ潤滑油が吸入される。Further, lubricating oil is sucked into the second gap B between the small-diameter end of the retainer and the small-diameter end of the inner race.
【０００７】 また、外輪の大径側端部と保持器の大
径側端部との間の第３隙間Ｃについては潤滑油の排出も
吸入もほとんど無い。[0007] Further, the third gap C between the large-diameter end of the outer ring and the large-diameter end of the cage hardly discharges or sucks lubricating oil.
【０００８】 また、保持器の大径側端部と内輪の大
径側端部との間の第４隙間Ｄから潤滑油が排出される。Further, the lubricating oil is discharged from a fourth gap D between the large-diameter end of the retainer and the large-diameter end of the inner race.
【０００９】本発明は、上記４つの実験結果に基づい
て、異物かみ込みを防いで軸受寿命を向上させることを
意図してなされたものである。The present invention has been made based on the results of the above four experiments, with the intention of preventing the entry of foreign matter and improving the bearing life.
【００１０】すなわち、請求項１の発明の円すいころ軸
受は、内,外輪間に複数の円すいころと、この円すいこ
ろを保持する保持器とを配設したオイル潤滑式の円すい
ころ軸受において、上記保持器の小径側端部と上記外輪
の小径側端部との間の第１隙間Ａを、上記保持器の小径
側端部と上記内輪の小径側端部との間の第２隙間Ｂより
も大きくし、上記第２隙間Ｂを、回転中に上記保持器が
上記内輪に接触しない範囲で近接するような値にしたこ
とを特徴としている。That is, the tapered roller bearing according to the first aspect of the present invention is an oil-lubricated tapered roller bearing having a plurality of tapered rollers between an inner ring and an outer ring, and a retainer for holding the tapered rollers. The first gap A between the small-diameter end of the cage and the small-diameter end of the outer ring is defined by the second gap B between the small-diameter end of the cage and the small-diameter end of the inner race. And the second gap B is set to a value such that the retainer comes close to the inner ring in a range where the retainer does not contact the inner ring during rotation.
【００１１】この請求項１の発明によれば、潤滑油を吸
入する第２隙間Ｂを上記値にしたから、小径側から大径
側への潤滑油の通過流量を抑えて、潤滑油によって運ば
れる異物かみ込みを防止し、軸受はくりを防いで軸受寿
命を向上できる。According to the first aspect of the present invention, since the second gap B for sucking the lubricating oil is set to the above value, the flow rate of the lubricating oil passing from the small diameter side to the large diameter side is suppressed, and the lubricating oil is conveyed. It is possible to prevent the foreign matter from being caught and prevent the bearing from breaking off, thereby improving the life of the bearing.
【００１２】また、小径側から大径側への潤滑油の通過
流量を増大させることなく、上記第２隙間Ｂよりも大き
くした第１隙間Ａから放熱させることができるから、軸
受の過熱を防止できる。Further, since the heat can be dissipated from the first gap A which is larger than the second gap B without increasing the flow rate of the lubricating oil from the small diameter side to the large diameter side, overheating of the bearing is prevented. it can.
【００１３】また、請求項２の発明は、請求項１に記載
の円すいころ軸受において、上記保持器の大径側端部と
上記外輪の大径側端部との間の第３隙間Ｃを、上記保持
器の大径側端部と上記内輪の大径側端部との間の第４隙
間Ｄよりも大きくし、上記第４隙間Ｄを、回転中に上記
保持器が上記内輪に接触しない範囲で近接するような値
にしたことを特徴としている。According to a second aspect of the present invention, in the tapered roller bearing according to the first aspect, the third gap C between the large-diameter end of the cage and the large-diameter end of the outer ring is formed. The fourth gap D between the large-diameter end of the cage and the large-diameter end of the inner ring is made larger, and the fourth gap D contacts the inner ring during rotation. It is characterized in that the values are set to be close to each other within a range not to be changed.
【００１４】この請求項２の発明によれば、潤滑油を吸
入する第２隙間Ｂだけでなく、潤滑油を排出する第４隙
間Ｄも保持器が内輪に接触しない範囲で近接するような
値にしたから、小径側から大径側への潤滑油通過量をよ
り一層抑えて、異物かみ込みを防止できる。According to the second aspect of the present invention, not only the second gap B for sucking the lubricating oil but also the fourth gap D for discharging the lubricating oil are set so that the cage is close to the inner ring in a range where the cage does not contact the inner ring. Therefore, the amount of the lubricating oil passing from the small-diameter side to the large-diameter side can be further suppressed, and the foreign matter can be prevented from being caught.
【００１５】また、上記第２隙間Ｂよりも大きくした第
１隙間Ａからだけでなく、上記第４隙間よりも大きくし
た第３隙間からも放熱させて冷却効果の増大を図れるか
ら、軸受の過熱をより一層確実に防止して、一層の寿命
向上を図れる。In addition, the cooling effect can be increased by dissipating heat not only from the first gap A, which is larger than the second gap B, but also from the third gap, which is larger than the fourth gap. Can be more reliably prevented, and the service life can be further improved.
【００１６】[0016]
【発明の実施の形態】以下、この発明を図示の実施の形
態により詳細に説明する。DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS Hereinafter, the present invention will be described in detail with reference to the illustrated embodiments.
【００１７】図１に、この発明の円すいころ軸受の実施
の形態を示す。この実施形態は、内輪１と外輪２と、内
輪１と外輪２との間に配設された複数の円すいころ３を
備えている。この円すいころ３は、保持器５の窓５ａに
嵌め込まれている。保持器５は、小径側端部として内径
側に屈曲した小径側鍔部６を有している。また、保持器
５は大径側端部として内径側に屈曲した大径側鍔部１２
を有している。FIG. 1 shows an embodiment of a tapered roller bearing according to the present invention. This embodiment includes an inner ring 1 and an outer ring 2, and a plurality of tapered rollers 3 disposed between the inner ring 1 and the outer ring 2. The tapered roller 3 is fitted into a window 5 a of the retainer 5. The retainer 5 has a small-diameter side flange 6 bent toward the inner diameter side as a small-diameter side end. The retainer 5 has a large-diameter side flange 12 bent to the inner diameter side as a large-diameter end.
have.
【００１８】また、内輪１は小径側鍔７と大径側鍔８を
有している。また、上記円すいころ３は、外輪２の軌道
面１０と内輪１の軌道面１１とに沿って走行することで
公転しながら自転するようになっている。The inner ring 1 has a small-diameter flange 7 and a large-diameter flange 8. The tapered rollers 3 run along the raceway surface 10 of the outer ring 2 and the raceway surface 11 of the inner ring 1 so as to revolve while revolving.
【００１９】そして、上記保持器５の小径側鍔部６と上
記内輪１の小径側鍔７との間の第２隙間Ｂを、０.１ｍ
ｍにして、回転中に保持器５が内輪１に接触しない範囲
で近接するような値にした。また、上記保持器５の小径
側鍔部６と上記外輪２の小径側端部１３との間の第１隙
間Ａを上記第２隙間Ｂよりも大きくした。The second gap B between the small-diameter flange 6 of the retainer 5 and the small-diameter flange 7 of the inner ring 1 is set to 0.1 m.
m was set to a value such that the cage 5 approached within a range where the cage 5 did not contact the inner ring 1 during rotation. The first gap A between the small-diameter side flange 6 of the retainer 5 and the small-diameter end 13 of the outer ring 2 is larger than the second gap B.
【００２０】また、上記保持器５の大径側鍔部１２と上
記内輪１の大径側鍔８との間の第４隙間Ｄを、０.１ｍ
ｍにして、回転中に保持器５が内輪１に接触しない範囲
で近接するような値にした。また、上記保持器５の大径
側鍔部１２と上記外輪２の大径側端部１７との間の第３
隙間Ｃを上記第４隙間Ｄよりも大きくした。The fourth gap D between the large-diameter flange 12 of the retainer 5 and the large-diameter flange 8 of the inner ring 1 is 0.1 m.
m was set to a value such that the cage 5 approached within a range where the cage 5 did not contact the inner ring 1 during rotation. Further, a third portion between the large-diameter side flange portion 12 of the retainer 5 and the large-diameter side end portion 17 of the outer race 2 is formed.
The gap C is larger than the fourth gap D.
【００２１】上記構成の円すいころ軸受によれば、潤滑
油を吸入する第１隙間Ｂを、保持器５が内輪１に接触し
ない範囲で近接するような値にしたから、小径側から大
径側への潤滑油の流量を抑えて、潤滑油によって運ばれ
る異物のかみ込みを防止し、軸受はくりを防いで軸受寿
命を向上できる。According to the tapered roller bearing having the above-described structure, the first gap B for sucking the lubricating oil is set to a value close to the range in which the retainer 5 does not contact the inner ring 1. The flow rate of the lubricating oil to the lubricating oil is suppressed, foreign matter carried by the lubricating oil is prevented from being entangled, and the bearing can be prevented from breaking off, thereby improving the life of the bearing.
【００２２】また、上記円すいころ軸受によれば、潤滑
油を吸入する第１隙間Ｂだけでなく、潤滑油を排出する
第２隙間Ｄも、保持器５が内輪１に接触しない範囲で近
接するような値にしたから、小径側から大径側への潤滑
油通過量を一層抑制でき、潤滑油で運ばれる異物のかみ
込みを防止できる。Further, according to the tapered roller bearing, not only the first gap B for sucking the lubricating oil but also the second gap D for discharging the lubricating oil are close to each other as long as the retainer 5 does not contact the inner ring 1. With such a value, the amount of lubricating oil passing from the small-diameter side to the large-diameter side can be further suppressed, and it is possible to prevent foreign substances carried by the lubricating oil from being caught.
【００２３】その上、上記円すいころ軸受によれば、第
１隙間Ａを第２隙間Ｂよりも大きくし、第３隙間Ｃを第
４隙間Ｄよりも大きくしたことによって、潤滑油通過量
を増大させることなく、放熱量を増大させて、冷却能力
を増大させることができる。したがって、軸受の過熱を
防止して、軸受寿命の向上を図れる。なお、上記隙間
Ａ,Ｂ,Ｄおよび隙間Ｃを変えた例について、潤滑油の流
れを確かめるための実験を行った結果を説明する。この
発明は、この実験結果に基づいてなされたものである。In addition, according to the tapered roller bearing, the first gap A is larger than the second gap B and the third gap C is larger than the fourth gap D, thereby increasing the amount of lubricating oil passing. Without doing so, it is possible to increase the amount of heat radiation and increase the cooling capacity. Therefore, overheating of the bearing can be prevented, and the life of the bearing can be improved. The results of an experiment for confirming the flow of the lubricating oil will be described for examples in which the gaps A, B, D and C are changed. The present invention has been made based on the results of this experiment.
【００２４】この実験は、図４に示すように、上記円す
いころ軸受２０を、シャフト２１に固定したリング２２
と環状外枠２３との間に取り付けた状態で行った。上記
シャフト２１は両端のころ軸受２５と２６でもって外壁
２７と２８に対して支持されている。また、シャフト２
１の一端部２１ａはカップリング３０でモーター３１の
回転軸３２に連結されている。また、上記外壁２７と外
枠２３の間と上記外壁２８と外枠２３の間には、透明な
円筒状外周板３３Ａと３３Ｂが嵌め込まれている。上記
外壁２７,２８および外枠２３と外周板３３がチャンバ
ー３５を構成しており、このチャンバー３５内に潤滑油
３７が充填されている。このチャンバー３５は、上記円
すいころ軸受２０を境界とする室４０と４１とからな
る。In this experiment, as shown in FIG. 4, the tapered roller bearing 20 was fixed to a shaft 22 by a ring 22.
It was carried out in a state of being attached between the outer frame 23 and the outer frame. The shaft 21 is supported on outer walls 27 and 28 by roller bearings 25 and 26 at both ends. Also, shaft 2
One end 21 a of one is connected to a rotating shaft 32 of a motor 31 by a coupling 30. Transparent cylindrical outer peripheral plates 33A and 33B are fitted between the outer wall 27 and the outer frame 23 and between the outer wall 28 and the outer frame 23. The outer walls 27 and 28, the outer frame 23, and the outer peripheral plate 33 form a chamber 35, and the chamber 35 is filled with a lubricating oil 37. The chamber 35 is composed of chambers 40 and 41 bounded by the tapered roller bearing 20.
【００２５】また、図示しないが、上記透明な外周板３
３Ａには室４０に連通していて鉛直上方に延びる透明な
管が取り付けられており、上記外周板３３Ｂには室４１
に連通していて鉛直上方に延びる別の透明な管が取り付
けられている。Although not shown, the transparent outer peripheral plate 3 is not shown.
A transparent tube communicating with the chamber 40 and extending vertically upward is attached to 3A, and a chamber 41 is attached to the outer peripheral plate 33B.
There is another transparent tube attached to and extending vertically upwards.
【００２６】この実験は、上記モーター３１を駆動し
て、上記室４０側の透明管の油面と上記室４１側の透明
管の油面との油面差を測定することによって、円すいこ
ろ軸受２０の小径側から大径側への油の流量つまりポン
プ能力の大きさを見積もるものである。In this experiment, the motor 31 was driven to measure the oil level difference between the oil level of the transparent tube on the chamber 40 side and the oil level of the transparent tube on the chamber 41 side. The flow rate of the oil from the small diameter side to the large diameter side of 20, that is, the magnitude of the pump capacity is estimated.
【００２７】この実験の結果を図２に示す。図２の特性
Ｃ０は標準の円すいころ軸受Ｘ１に比べて隙間Ａを狭め
た軸受Ｘ０の特性であり、特性Ｃ１は上記実施形態に比
べて隙間Ａを広げた標準軸受Ｘ１の特性である。特性Ｃ
２は上記標準軸受Ｘ１に比べて隙間Ｃを狭めた軸受Ｘ２
の特性である。また、特性Ｃ３は上記標準軸受Ｘ１に比
べて隙間Ｄをやや狭めた軸受Ｘ３の特性である。また、
特性Ｃ４は上記軸受Ｘ１に比べて隙間Ｂを狭めた軸受Ｘ
４の特性である。なお、この標準軸受Ｘ１は上記実施形
態に比べて隙間Ａが小さく設定され、隙間Ｂが大きく設
定され、隙間Ｃが小さく設定され、隙間Ｄが大きく設定
されている。FIG. 2 shows the results of this experiment. A characteristic C0 in FIG. 2 is a characteristic of the bearing X0 in which the gap A is narrowed as compared with the standard tapered roller bearing X1, and a characteristic C1 is a characteristic of the standard bearing X1 in which the gap A is widened as compared with the above embodiment. Characteristic C
2 is a bearing X2 having a smaller gap C than the standard bearing X1.
It is the characteristic of. The characteristic C3 is a characteristic of the bearing X3 in which the gap D is slightly narrowed as compared with the standard bearing X1. Also,
The characteristic C4 is a bearing X having a smaller gap B than the bearing X1.
4 is the characteristic. In this standard bearing X1, the gap A is set smaller, the gap B is set larger, the gap C is set smaller, and the gap D is set larger than in the above embodiment.
【００２８】図２より分かるように、上記軸受Ｘ０の特
性Ｃ０は回転数全域に亘って、油面差が最も大きく、ポ
ンプ能力が最も大きい。そして、特性Ｃ１は、隙間Ａを
広げたことによって油面差が小さくなったことを示す。
これは、隙間Ａからは潤滑油が排出されていることを示
し、これは、所定のマーカーを用いた室４０内の潤滑油
の流れの観察によっても確認できた。また、特性Ｃ２
は、隙間Ｃを狭めても油面差はほとんど変化しなかった
ことを示している。この結果は、隙間Ｃが潤滑油のポン
プ作用にほとんど寄与していないことを示す。また、特
性Ｃ３は、隙間Ｄをやや狭めると油面差がやや小さくな
ったことを示す。この結果は、隙間Ｄから潤滑油が排出
されていることを示す。また、特性Ｃ４は、隙間Ｂを狭
めると油面差が小さくなったことを示す。この結果は、
隙間Ｂから潤滑油が吸入されていることを示す。As can be seen from FIG. 2, the characteristic C0 of the bearing X0 has the largest oil level difference and the largest pumping ability over the entire rotational speed range. The characteristic C1 indicates that the oil level difference is reduced by increasing the gap A.
This indicates that the lubricating oil has been discharged from the gap A, which was also confirmed by observing the flow of the lubricating oil in the chamber 40 using a predetermined marker. The characteristic C2
Indicates that the oil level difference hardly changed even if the gap C was narrowed. This result indicates that the gap C hardly contributes to the pumping action of the lubricating oil. The characteristic C3 indicates that when the gap D is slightly narrowed, the oil level difference is slightly reduced. This result indicates that the lubricating oil is discharged from the gap D. The characteristic C4 indicates that the oil level difference was reduced when the gap B was narrowed. The result is
This indicates that lubricating oil is being sucked from the gap B.
【００２９】すなわち、これらの実験結果から、次の
,,,のことが分かる。That is, from the results of these experiments, the following
You can see ,,,.
【００３０】 図３に示すように、回転時に、外輪の
小径側端部と保持器の小径側端部との間の隙間Ａから潤
滑油が排出される。As shown in FIG. 3, during rotation, lubricating oil is discharged from a gap A between the small-diameter end of the outer ring and the small-diameter end of the cage.
【００３１】 また、保持器の小径側端部と内輪の小
径側端部との間の隙間Ｂへ潤滑油が吸入される。Further, lubricating oil is sucked into the gap B between the small-diameter end of the retainer and the small-diameter end of the inner race.
【００３２】 また、外輪の大径側端部と保持器の大
径側端部との間の隙間Ｃについては潤滑油の排出も吸入
もほとんど無い。Further, in the gap C between the large-diameter end of the outer ring and the large-diameter end of the retainer, there is almost no discharge or suction of lubricating oil.
【００３３】 また、保持器の大径側端部と内輪の大
径側端部との間の隙間Ｄから潤滑油が排出される。Further, the lubricating oil is discharged from the gap D between the large-diameter end of the retainer and the large-diameter end of the inner race.
【００３４】この実施形態によれば、上記第２隙間Ｂと
第４隙間Ｄとを、保持器５が内輪１に接触しない範囲で
近接するような値に設定したから、ポンプ作用をできる
だけ小さくして、円すいころ３を通過する潤滑油の量を
できるだけ抑制し、潤滑油で運ばれる異物の噛み込みを
抑えて、軸受はくりを抑えることができる。According to this embodiment, since the second gap B and the fourth gap D are set to values close to each other in a range where the retainer 5 does not contact the inner ring 1, the pump action is reduced as much as possible. Thus, the amount of the lubricating oil passing through the tapered rollers 3 can be suppressed as much as possible, the biting of foreign substances carried by the lubricating oil can be suppressed, and the bearing can be prevented from turning.
【００３５】また、第１隙間Ａを第２隙間Ｂより大きく
し、第３隙間Ｃを第４隙間Ｄよりも大きくしたから、こ
の第１隙間Ａと第３隙間Ｃからの放熱量の増大を図り、
冷却効果を増大させて、軸受の過熱を防止して、一層の
寿命の向上を図れる。Further, since the first gap A is larger than the second gap B and the third gap C is larger than the fourth gap D, the amount of heat radiation from the first gap A and the third gap C is increased. Plan,
By increasing the cooling effect, the bearing can be prevented from being overheated, and the life can be further improved.
【００３６】尚、上記実施形態では、保持器５の小径側
端部および大径側端部を鍔部６および１２で構成した
が、上記小径側端部および大径側端部を厚肉部で構成し
てもよい。In the above-described embodiment, the small-diameter end and the large-diameter end of the retainer 5 are formed by the flanges 6 and 12. However, the small-diameter end and the large-diameter end are formed by thick portions. May be configured.
【００３７】また、上記実施形態では、第２隙間Ｂおよ
び第４の隙間Ｄの寸法を０.１ｍｍとしたが、この隙間
の寸法は、０.１ｍｍ〜０.５ｍｍ程度の範囲で適宜調整
してよい。In the above embodiment, the dimensions of the second gap B and the fourth gap D are set to 0.1 mm, but the dimensions of the gap are appropriately adjusted within a range of about 0.1 mm to 0.5 mm. May be.
【００３８】[0038]
【発明の効果】以上より明らかなように、請求項１の発
明の円すいころ軸受は、保持器の小径側端部と外輪の小
径側端部との間の第１隙間Ａを、保持器の小径側端部と
内輪の小径側端部との間の第２隙間Ｂよりも大きくし、
第２隙間Ｂを、回転中に保持器が上記内輪に接触しない
範囲で近接するような値にした。As is apparent from the above description, the tapered roller bearing according to the first aspect of the present invention has the first gap A between the small-diameter end of the cage and the small-diameter end of the outer ring, and Larger than the second gap B between the small diameter end and the small diameter end of the inner ring,
The second gap B was set to a value such that the cage approached within a range where the cage did not contact the inner ring during rotation.
【００３９】この請求項１の発明によれば、潤滑油を吸
入する第２隙間Ｂを上記値にしたから、小径側から大径
側への潤滑油の通過流量を抑えて、潤滑油によって運ば
れる異物かみ込みを防止し、軸受はくりを防いで軸受寿
命を向上できる。According to the first aspect of the present invention, since the second gap B for sucking the lubricating oil is set to the above value, the flow rate of the lubricating oil from the small diameter side to the large diameter side is suppressed, and the lubricating oil is conveyed. It is possible to prevent the foreign matter from being caught and prevent the bearing from breaking off, thereby improving the life of the bearing.
【００４０】また、小径側から大径側への潤滑油の通過
流量を増大させることなく、上記第２隙間Ｂよりも大き
くした第１隙間Ａから放熱させて軸受の過熱を防止でき
る。Further, without increasing the flow rate of the lubricating oil from the small diameter side to the large diameter side, heat can be radiated from the first gap A which is larger than the second gap B to prevent overheating of the bearing.
【００４１】また、請求項２の発明は、請求項１に記載
の円すいころ軸受において、保持器の大径側端部と外輪
の大径側端部との間の第３隙間Ｃを、保持器の大径側端
部と内輪の大径側端部との間の第４隙間Ｄよりも大きく
し、第４隙間Ｄを、回転中に上記保持器が上記内輪に接
触しない範囲で近接するような値にした。According to a second aspect of the present invention, in the tapered roller bearing according to the first aspect, the third gap C between the large-diameter end of the cage and the large-diameter end of the outer ring is retained. The fourth gap D between the large-diameter end of the vessel and the large-diameter end of the inner ring is made larger, and the fourth gap D is approached within a range where the retainer does not contact the inner ring during rotation. It was set to such a value.
【００４２】この請求項２の発明によれば、潤滑油を吸
入する第２隙間Ｂだけでなく、潤滑油を排出する第４隙
間Ｄも保持器が内輪に接触しない範囲で近接するような
値にしたから、小径側から大径側への潤滑油通過量をよ
り一層抑えて、異物かみ込みを防止できる。According to the second aspect of the present invention, not only the second gap B for sucking the lubricating oil but also the fourth gap D for discharging the lubricating oil are set so that the retainers are close to each other within a range where the cage does not contact the inner ring. Therefore, the amount of the lubricating oil passing from the small-diameter side to the large-diameter side can be further suppressed, and the foreign matter can be prevented from being caught.
【００４３】また、上記第２隙間Ｂよりも大きくした第
１隙間Ａからだけでなく、上記第４隙間よりも大きくし
た第３隙間からも放熱させて冷却効果の増大を図れるか
ら、軸受の過熱をより一層確実に防止して、一層の寿命
向上を図れる。In addition, the cooling effect can be increased not only from the first gap A, which is larger than the second gap B, but also from the third gap, which is larger than the fourth gap. Can be more reliably prevented, and the service life can be further improved.
【図１】 この発明の円すいころ軸受の実施の形態の要
部断面図である。FIG. 1 is a sectional view of a main part of an embodiment of a tapered roller bearing according to the present invention.
【図２】 円すいころ軸受の潤滑油流れ確認実験結果を
示す特性図である。FIG. 2 is a characteristic diagram showing results of an experiment for confirming lubricating oil flow of a tapered roller bearing.
【図３】 上記潤滑油流れ確認実験結果から判明した各
隙間Ａ,Ｂ,Ｃ,Ｄでの潤滑油の流れの方向を示す模式図
である。FIG. 3 is a schematic diagram showing the direction of the flow of lubricating oil in each of the gaps A, B, C, and D found from the results of the lubricating oil flow confirmation experiment.
【図４】 上記潤滑油流れ確認実験の実験装置を示す要
部断面図である。FIG. 4 is a cross-sectional view of a main part showing an experimental apparatus for the lubricating oil flow confirmation experiment.
１…内輪、２…外輪、３…円すいころ、５…保持器、５
ａ…窓、６…小径側鍔部、７…小径側鍔、８…大径側
鍔、１０,１１…軌道面、１２…大径側鍔部、１３…小
径側端部、１５…小径側端面、１７…大径側端部、２０
…円すいころ軸受、Ａ,Ｂ,Ｃ,Ｄ…隙間。DESCRIPTION OF SYMBOLS 1 ... Inner ring, 2 ... Outer ring, 3 ... Tapered roller, 5 ... Cage, 5
a: window, 6: small-diameter flange, 7: small-diameter flange, 8: large-diameter flange, 10, 11: track surface, 12: large-diameter flange, 13: small-diameter end, 15: small-diameter side End face, 17 ... Large diameter end, 20
... tapered roller bearings, A, B, C, D ... gaps.
Claims (2)
円すいころを保持する保持器とを配設したオイル潤滑式
の円すいころ軸受において、 上記保持器の小径側端部と上記外輪の小径側端部との間
の第１隙間Ａを、上記保持器の小径側端部と上記内輪の
小径側端部との間の第２隙間Ｂよりも大きくし、 上記第２隙間Ｂを、回転中に上記保持器が上記内輪に接
触しない範囲で近接するような値にしたことを特徴とす
る円すいころ軸受。1. An oil-lubricated tapered roller bearing having a plurality of tapered rollers between an inner ring and an outer ring, and a retainer for holding the tapered rollers, wherein a small-diameter end of the retainer and an outer ring of the outer ring are provided. The first gap A between the small diameter end and the second gap B between the small diameter end of the retainer and the small diameter end of the inner ring is made larger. A tapered roller bearing characterized in that the value is set so that the cage comes close to the inner ring without rotating while rotating.
て、 上記保持器の大径側端部と上記外輪の大径側端部との間
の第３隙間Ｃを、上記保持器の大径側端部と上記内輪の
大径側端部との間の第４隙間Ｄよりも大きくし、 上記第４隙間Ｄを、回転中に上記保持器が上記内輪に接
触しない範囲で近接するような値にしたことを特徴とす
る円すいころ軸受。2. The tapered roller bearing according to claim 1, wherein a third gap C between a large-diameter end of the cage and a large-diameter end of the outer race is provided with a large diameter of the cage. The fourth gap D between the side end and the large-diameter end of the inner ring is set to be larger than the fourth gap D so that the retainer comes close to the inner ring in a range where the retainer does not contact the inner ring during rotation. Tapered roller bearings characterized by a value.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP24764596A JPH1089353A (en) | 1996-09-19 | 1996-09-19 | Tapered roller bearing |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP24764596A JPH1089353A (en) | 1996-09-19 | 1996-09-19 | Tapered roller bearing |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JPH1089353A true JPH1089353A (en) | 1998-04-07 |
Family
ID=17166581
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP24764596A Pending JPH1089353A (en) | 1996-09-19 | 1996-09-19 | Tapered roller bearing |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPH1089353A (en) |
Cited By (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| EP1580028A2 (en) | 2004-03-25 | 2005-09-28 | Koyo Seiko Co., Ltd. | Tapered roller bearing |
| JP2007138992A (en) * | 2005-11-15 | 2007-06-07 | Jtekt Corp | Liquid lubricated tapered roller bearing device |
| JP2007315552A (en) * | 2006-05-29 | 2007-12-06 | Ntn Corp | Tapered roller bearing |
| WO2008015829A1 (en) * | 2006-08-01 | 2008-02-07 | Ntn Corporation | Tapered roller bearing |
| JP2009287593A (en) * | 2008-05-27 | 2009-12-10 | Jtekt Corp | Tapered roller bearing |
| US7645074B2 (en) | 2005-04-28 | 2010-01-12 | Jtekt Corporation | Fluid-lubricated type tapered roller bearing device and vehicle pinion shaft supporting assembly |
| WO2016194981A1 (en) * | 2015-06-05 | 2016-12-08 | Ntn株式会社 | Tapered roller bearing |
| JP2017003109A (en) * | 2015-06-05 | 2017-01-05 | Ntn株式会社 | Conical roller bearing |
| DE102006032750B4 (en) * | 2005-07-15 | 2017-10-26 | Ntn Corp. | Tapered roller bearings |
-
1996
- 1996-09-19 JP JP24764596A patent/JPH1089353A/en active Pending
Cited By (17)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US7320550B2 (en) | 2004-03-25 | 2008-01-22 | Jtekt Corporation | Tapered roller bearing |
| US7175351B2 (en) | 2004-03-25 | 2007-02-13 | Koyo Seiko Co., Ltd. | Tapered roller bearing |
| EP1580028A2 (en) | 2004-03-25 | 2005-09-28 | Koyo Seiko Co., Ltd. | Tapered roller bearing |
| US7645074B2 (en) | 2005-04-28 | 2010-01-12 | Jtekt Corporation | Fluid-lubricated type tapered roller bearing device and vehicle pinion shaft supporting assembly |
| DE102006032750B4 (en) * | 2005-07-15 | 2017-10-26 | Ntn Corp. | Tapered roller bearings |
| JP2007138992A (en) * | 2005-11-15 | 2007-06-07 | Jtekt Corp | Liquid lubricated tapered roller bearing device |
| JP4635838B2 (en) * | 2005-11-15 | 2011-02-23 | 株式会社ジェイテクト | Liquid lubricated tapered roller bearing device |
| US8876397B2 (en) | 2005-11-15 | 2014-11-04 | Jtekt Corporation | Liquid lubricating tapered roller bearing device |
| JP2007315552A (en) * | 2006-05-29 | 2007-12-06 | Ntn Corp | Tapered roller bearing |
| JP4651578B2 (en) * | 2006-05-29 | 2011-03-16 | Ｎｔｎ株式会社 | Tapered roller bearings |
| WO2008015829A1 (en) * | 2006-08-01 | 2008-02-07 | Ntn Corporation | Tapered roller bearing |
| JP2008038927A (en) * | 2006-08-01 | 2008-02-21 | Ntn Corp | Tapered roller bearing |
| US8152383B2 (en) | 2006-08-01 | 2012-04-10 | Ntn Corporation | Tapered roller bearing |
| DE112007001806B4 (en) * | 2006-08-01 | 2020-04-23 | Ntn Corp. | Tapered roller bearings |
| JP2009287593A (en) * | 2008-05-27 | 2009-12-10 | Jtekt Corp | Tapered roller bearing |
| JP2017003109A (en) * | 2015-06-05 | 2017-01-05 | Ntn株式会社 | Conical roller bearing |
| WO2016194981A1 (en) * | 2015-06-05 | 2016-12-08 | Ntn株式会社 | Tapered roller bearing |
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