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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