JPH1089352A - Tapered roller bearing - Google Patents
Tapered roller bearingInfo
- Publication number
- JPH1089352A JPH1089352A JP8247642A JP24764296A JPH1089352A JP H1089352 A JPH1089352 A JP H1089352A JP 8247642 A JP8247642 A JP 8247642A JP 24764296 A JP24764296 A JP 24764296A JP H1089352 A JPH1089352 A JP H1089352A
- Authority
- JP
- Japan
- Prior art keywords
- gap
- lubricating oil
- tapered roller
- diameter side
- 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.)
- Granted
Links
- 230000001050 lubricating effect Effects 0.000 abstract description 5
- 239000000314 lubricant Substances 0.000 abstract 4
- 239000010687 lubricating oil Substances 0.000 description 62
- 238000005461 lubrication Methods 0.000 description 15
- 239000003921 oil Substances 0.000 description 12
- 238000010586 diagram Methods 0.000 description 6
- 230000007423 decrease Effects 0.000 description 4
- 230000002093 peripheral effect Effects 0.000 description 4
- 238000005086 pumping Methods 0.000 description 4
- 238000013459 approach Methods 0.000 description 3
- 230000000052 comparative effect Effects 0.000 description 2
- 238000012790 confirmation Methods 0.000 description 2
- 230000008878 coupling Effects 0.000 description 1
- 238000010168 coupling process Methods 0.000 description 1
- 238000005859 coupling reaction Methods 0.000 description 1
- 239000003550 marker Substances 0.000 description 1
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
- F16C33/30—Parts of ball or roller bearings
- F16C33/66—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
-
- 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
-
- 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
- F16C33/667—Details of supply of the liquid to the bearing, e.g. passages or nozzles related to conditioning, e.g. cooling, filtering
-
- 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
- F16C2300/00—Application independent of particular apparatuses
- F16C2300/02—General use or purpose, i.e. no use, purpose, special adaptation or modification indicated or a wide variety of uses mentioned
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
コントロールして潤滑性能を向上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 lubricating oil flow and improving lubrication performance.
【０００２】[0002]
【従来の技術】従来、この種の円すいころ軸受として
は、図７に示すものがある(実開昭５８−１５０６２０
号公報)。この円すいころ軸受は、保持器１０１の大径
側端部１０１Ａと内輪１０２の大径側端部１０２Ａとの
間の第１隙間Ｄが、保持器１０１の小径側端部１０１Ｂ
と内輪１０２の小径側端部１０２Ｂとの間の第２隙間Ｂ
よりも小さく設定されている。また、外輪１０３の小径
側端部１０３Ｂと保持器１０１の小径側端部１０１Ｂと
の間の第３隙間Ａが上記第２隙間Ｂよりも小さく設定さ
れている。2. Description of the Related Art Conventionally, as this type of tapered roller bearing, there is one shown in FIG.
Publication). In this tapered roller bearing, the first gap D between the large-diameter end 101A of the retainer 101 and the large-diameter end 102A of the inner ring 102 is smaller than the small-diameter end 101B of the retainer 101.
Gap B between the inner ring 102 and the small-diameter end 102B of the inner ring 102
It is set smaller than. The third gap A between the small-diameter end 103B of the outer ring 103 and the small-diameter end 101B of the retainer 101 is set smaller than the second gap B.
【０００３】上記円すいころ軸受は、回転時の遠心力で
もって潤滑油を上記第２隙間Ｂから隙間Ｃに向かって円
滑に流動させ、これにより潤滑性能を向上させることを
意図したものである。[0003] The tapered roller bearing is intended to smoothly lubricate the lubricating oil from the second gap B toward the gap C by centrifugal force during rotation, thereby improving the lubrication performance.
【０００４】[0004]
【発明が解決しようとする課題】しかしながら、本発明
者らによる潤滑油流れの確認実験によれば、上記第２隙
間Ｂから隙間Ｃに向かう矢印１０５のような流れは実質
的に存在しないことが判明した。したがって、上記従来
のような円すいころ軸受では、潤滑性能の向上を期待す
ることができない。However, according to experiments conducted by the present inventors to confirm the flow of lubricating oil, it has been found that there is substantially no flow as indicated by the arrow 105 from the second gap B to the gap C. found. Therefore, improvement of lubrication performance cannot be expected in the above-described conventional tapered roller bearing.
【０００５】そこで、この発明の目的は、潤滑油を小径
側から大径側にスムーズに流動させることができ、潤滑
性能の向上を図ることができる円すいころ軸受を提供す
ることにある。An object of the present invention is to provide a tapered roller bearing capable of smoothly flowing lubricating oil from a small diameter side to a large diameter side and improving lubrication performance.
【０００６】[0006]
【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.
【０００７】 図４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３隙間Ａか
ら潤滑油が排出される。As shown in FIG. 4, during rotation, lubricating oil is discharged from a third gap A between the small-diameter end of the outer race and the small-diameter end of the cage.
【０００８】 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。In addition, 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.
【０００９】 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。[0009] Furthermore, the clearance C between the large-diameter end of the outer ring and the large-diameter end of the cage hardly discharges or sucks lubricating oil.
【００１０】 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１隙間Ｄから潤滑油が排出される。Further, the lubricating oil is discharged from the first gap D between the large-diameter end of the retainer and the large-diameter end of the inner race.
【００１１】本発明は、上記４つの実験結果に基づい
て、回転時の潤滑性能の向上を意図してなされたもので
ある。The present invention has been made with the aim of improving the lubrication performance during rotation based on the above four experimental results.
【００１２】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、上記保持器の大径側端部と上記内輪
の大径側端部との間の第１隙間Ｄが、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、上記第２隙間Ｂが、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３隙間Ａよりも大き
く、上記第３隙間Ａを、上記保持器が上記外輪に接触し
ない範囲で保持器が外輪に近接するような値に設定した
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 in which a plurality of tapered rollers and a retainer for holding the tapered rollers are disposed between inner and outer rings. A first gap D between the large-diameter end of the cage and the large-diameter end of the inner race is a second gap between the small-diameter end of the cage and the small-diameter end of the inner race. B, the second gap B is larger than the third gap A between the small-diameter end of the cage and the small-diameter end of the outer ring, and the third gap A is defined by the cage. Is set to a value such that the retainer approaches the outer ring within a range not to contact the outer ring.
【００１３】この請求項１の発明によれば、回転時に潤
滑油が排出される第１隙間Ｄを、回転時に潤滑油が吸入
される第２隙間Ｂよりも大きくした。したがって、第２
隙間Ｂから吸入した潤滑油を軸受内に滞らせることな
く、スムーズに第１隙間Ｄから排出させることができ
る。したがって、潤滑油の流れを円滑にして、潤滑性能
を向上させることができる。According to the first aspect of the present invention, the first gap D from which the lubricating oil is discharged during rotation is made larger than the second gap B from which the lubricating oil is sucked during rotation. Therefore, the second
The lubricating oil sucked from the gap B can be smoothly discharged from the first gap D without stagnation in the bearing. Therefore, the flow of the lubricating oil can be made smooth, and the lubricating performance can be improved.
【００１４】また、潤滑油が吸入される小径側の第２隙
間Ｂを、同じ小径側にあって潤滑油が排出される第３隙
間Ａよりも大きくしたから、円すいころを経由せずに第
２隙間Ｂから第３隙間Ａへ流れるの潤滑油の量を少なく
して、摺動部分への潤滑油供給量の増大を図れ、潤滑性
能の向上を図れる。Further, since the second gap B on the small diameter side where the lubricating oil is sucked is made larger than the third gap A on the same small diameter side where the lubricating oil is discharged, the second gap B is formed without passing through the tapered rollers. By reducing the amount of lubricating oil flowing from the second gap B to the third gap A, the amount of lubricating oil supplied to the sliding portion can be increased, and the lubrication performance can be improved.
【００１５】また、上記第３隙間Ａを保持器と外輪とが
接触しない範囲で保持器が外輪に近接するような値にし
たから、第２隙間Ｂから吸入された潤滑油が円すいころ
を通過せずに第３隙間Ａから排出されてしまうことを防
げる。したがって、第２隙間Ｂから吸入した潤滑油を最
大限に軸受の摺動部分に導入でき、潤滑性能の向上を図
れる。Since the third gap A is set to a value such that the cage approaches the outer ring in a range where the cage does not contact the outer ring, the lubricating oil sucked from the second gap B passes through the tapered rollers. It can be prevented from being discharged from the third gap A without doing so. Therefore, the lubricating oil sucked from the second gap B can be introduced to the sliding portion of the bearing to the maximum, and the lubrication performance can be improved.
【００１６】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、上記第３隙間Ａを、０.１
乃至０.５ｍｍに設定されている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 A is set to 0.1.
From 0.5 mm to 0.5 mm.
【００１７】この請求項２の発明によれば、回転の保持
器と外輪との接触を防ぎつつ、上記第３隙間Ａから潤滑
油が排出されることを最大限に抑制して、潤滑に寄与し
ない第２隙間Ｂから第３隙間Ａへの無駄な潤滑油の流れ
を最小にできる。したがって、潤滑性能の向上を図れ
る。According to the second aspect of the present invention, the contact between the rotating cage and the outer ring is prevented, and at the same time, the discharge of the lubricating oil from the third gap A is suppressed to the maximum, thereby contributing to lubrication. The wasteful flow of lubricating oil from the second gap B to the third gap A, which is not performed, can be minimized. Therefore, the lubrication performance can be improved.
【００１８】また、請求項３の発明によれば、請求項１
または２に記載の円すいころ軸受において、上記円すい
ころの小径側端面の中心の公転円の直径よりも、上記保
持器の小径側端部の内径側直径が小さくなるように設定
されていることを特徴としている。According to the invention of claim 3, according to claim 1,
Or the tapered roller bearing according to 2, wherein the diameter of the inner diameter side of the small diameter side end of the retainer is set to be smaller than the diameter of the revolving circle at the center of the small diameter side end face of the tapered roller. Features.
【００１９】発明者らは、保持器の小径側端部の内径側
直径を円すいころの小径側端部中心の公転円直径よりも
小さく設定したときに、第２隙間Ｂから吸入される潤滑
油量が極大値を示すことを実験で確認することができ
た。したがって、請求項３の発明によれば、第２隙間Ｂ
の広げ過ぎによる潤滑油吸入量の減少を抑えることがで
き、潤滑性能の向上を図れる。When the inner diameter of the small-diameter end of the cage is set smaller than the revolving circle diameter at the center of the small-diameter end of the tapered roller, the lubricating oil sucked from the second gap B is set. It was confirmed by experiment that the amount showed a maximum value. Therefore, according to the invention of claim 3, the second gap B
It is possible to suppress a decrease in the lubricating oil suction amount due to excessive expansion of the lubricating oil, thereby improving lubricating performance.
【００２０】[0020]
【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.
【００２１】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、内径側に屈曲した鍔部
６を小径側に有している。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。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 flange 6 bent to the inner diameter side on the small diameter side. The inner ring 1 has a small-diameter flange 7 and a large-diameter flange 8. The tapered roller 3 is
By running along the raceway surface 10 of the outer race 2 and the raceway surface 11 of the inner race 1, the robot rotates while revolving.
【００２２】そして、上記保持器５の大径側端部１２と
上記内輪１の大径側端部としての大径側鍔８との間の第
１隙間Ｄが、上記保持器５の小径側端部としての鍔部６
と内輪１の小径側鍔７との間の第２隙間Ｂよりも大きく
設定されている。The first gap D between the large-diameter end 12 of the retainer 5 and the large-diameter flange 8 as the large-diameter end of the inner race 1 is defined by the small-diameter side of the retainer 5. Flange 6 as end
It is set to be larger than the second gap B between the inner ring 1 and the small diameter side flange 7.
【００２３】また、上記第２隙間Ｂは、上記保持器５の
鍔部６と外輪２の小径側端部１３との間の第３隙間Ａよ
りも大きく設定されている。また、上記第３隙間Ａを、
０.１ｍｍ乃至０.５ｍｍに設定し、上記保持器５が上記
外輪２に接触しない範囲で保持器５が外輪２に近接する
ような値にした。The second gap B is set to be larger than the third gap A between the flange 6 of the retainer 5 and the small-diameter end 13 of the outer ring 2. Further, the third gap A is
The value was set to 0.1 mm to 0.5 mm so that the cage 5 approached the outer ring 2 within a range where the cage 5 did not contact the outer ring 2.
【００２４】また、上記円すいころ３の小径側端面１５
の中心の公転円の直径よりも、上記保持器５の鍔部６の
内径側直径が小さくなるように設定されている。Also, the small diameter side end face 15 of the tapered roller 3
The diameter of the inner diameter side of the flange 6 of the retainer 5 is set to be smaller than the diameter of the revolving circle at the center of.
【００２５】上記構成の円すいころ軸受および比較例と
して上記隙間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。なお、上記隙間Ｃは、図１に示すように、保
持器５の大径側端部１２と外輪の大径側端部１７との間
の隙間である。The results of an experiment for confirming the flow of lubricating oil will be described with respect to the tapered roller bearing having the above configuration and an example in which the gaps A, B, D and C are changed as a comparative example. The gap C is a gap between the large-diameter end 12 of the retainer 5 and the large-diameter end 17 of the outer race, as shown in FIG.
【００２６】この実験は、図６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. 6, the tapered roller bearing 20 was fixed to a shaft 21 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.
【００２７】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.
【００２８】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.
【００２９】この実験の結果を図２に示す。図２の特性
Ｃ０が上記実施形態の円すいころ軸受の特性であり、特
性Ｃ１は上記実施形態に比べて第３隙間Ａを広げた標準
軸受Ｘ１の特性である。また、特性Ｃ２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に比べて第１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に比べて第２隙間Ｂを狭めた軸受Ｘ４の特性
である。FIG. 2 shows the results of this experiment. The characteristic C0 in FIG. 2 is the characteristic of the tapered roller bearing of the above embodiment, and the characteristic C1 is the characteristic of the standard bearing X1 in which the third gap A is widened as compared with the above embodiment. The characteristic C2 is a characteristic of the bearing X2 in which the gap C is narrower than the standard bearing X1. The characteristic C3 is a characteristic of the bearing X3 in which the first gap D is slightly narrowed as compared with the standard bearing X1. The characteristic C4 is a characteristic of the bearing X4 in which the second gap B is narrowed as compared with the bearing X1.
【００３０】図２より分かるように、上記実施形態の特
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から、小径側から大径側への潤滑
油の流量が最も大きくて、潤滑性能を最も大きくでき
る。そして、特性Ｃ１は、第３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、第３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、第
１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、第１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、第２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、
第２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, since the characteristic C0 of the above embodiment has the largest oil level difference and the largest pumping ability over the entire rotation speed range, the flow rate of the lubricating oil from the small diameter side to the large diameter side is large. Is the largest, and the lubrication performance can be maximized. The characteristic C1 indicates that the oil level difference is reduced by widening the third gap A. This indicates that the lubricating oil was discharged from the third gap A, which could be confirmed by observing the flow of the lubricating oil in the chamber 40 using a predetermined marker. Further, the characteristic C2 indicates that the oil level difference hardly changed even when 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 first gap D is slightly narrowed, the oil level difference is slightly reduced. This result indicates that the lubricating oil has been discharged from the first gap D. Further, the characteristic C4 indicates that the oil level difference was reduced when the second gap B was narrowed. The result is
This indicates that lubricating oil is being sucked in from the second gap B.
【００３１】これらの実験結果から次の(i),(ii),(iii)
のことが分かる。From these experimental results, the following (i), (ii), (iii)
You can see that.
【００３２】(i) 回転時に潤滑油が排出される第１隙間
Ｄを、回転時に潤滑油が吸入する第２隙間Ｂよりも大き
くすることによって、第２隙間Ｂから吸入した潤滑油を
軸受内に滞らせることなく、スムーズに第１隙間Ｄから
排出できる。(I) By making the first gap D from which the lubricating oil is discharged during rotation larger than the second gap B into which the lubricating oil is sucked during rotation, the lubricating oil sucked from the second gap B is supplied into the bearing. Can be smoothly discharged from the first gap D without delay.
【００３３】(ii) 潤滑油が吸入される小径側の第２隙
間Ｂを、同じ小径側にあって潤滑油が排出される第３隙
間Ａよりも大きくすることによって、軸受への潤滑油供
給量の増大を図れる。(Ii) By making the second gap B on the small diameter side where the lubricating oil is sucked larger than the third gap A on the same small diameter side where the lubricating oil is discharged, the lubricating oil is supplied to the bearing. The amount can be increased.
【００３４】(iii) 第３隙間Ａを保持器と外輪とが接触
せずに近接するような値にすることによって、第２隙間
Ｂから吸入された潤滑油が円すいころ３を通らずに第３
隙間Ａから排出されてしまうことを防げる。(Iii) By setting the third gap A to a value such that the cage and the outer ring are close to each other without contacting each other, the lubricating oil sucked from the second gap B does not pass through the tapered rollers 3 and 3
It can be prevented from being discharged from the gap A.
【００３５】したがって、この実施形態によれば、ポン
プ作用を最大に発揮させて、円すいころ３を通過する潤
滑油の流れが速く、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。Therefore, according to this embodiment, the pumping action is maximized, the flow of the lubricating oil passing through the tapered rollers 3 is fast, foreign matter is prevented from being caught, and the bearing can be prevented from being cut off. .
【００３６】また、円すいころ３に常に新たな潤滑油を
供給でき、潤滑性能を向上させることができる。Further, new lubricating oil can always be supplied to the tapered rollers 3, and the lubricating performance can be improved.
【００３７】また、上記図６に示した実験において、上
記実施形態の円すいころ軸受の第２隙間Ｂを変化させた
ときの油面差を測定した結果を図３に示す。なお、図３
の実験では、モータの回転数は２５００ｒｐｍとした。
上記実施の形態では、第２隙間Ｂを１.５ｍｍに設定し
て、油面差が極大値になるようにした。図５(Ｂ)に示す
ように、第２隙間Ｂ＝１.５ｍｍに設定すれば、保持器
５の鍔部６の内径側直径Ｙ１が円すいころ３の小径側端
面１５の中心の公転円の直径Ｙ２よりも小さくなってい
る。そして、第２隙間Ｂを１.５ｍｍよりも大きくし
て、図５(Ｃ)に示すように設定した場合には、第２隙間
Ｂからの潤滑油の吸入量は極大値から減少する。また、
第２隙間Ｂを１.５ｍｍよりも小さくして、図５(Ａ)に
示すように設定した場合にも、第２隙間Ｂからの潤滑油
の吸入量は極大値から減少する。なお、このことは、モ
ータの回転数を変えても、同様に再現することが実験で
確かめられている。FIG. 3 shows the result of measuring the oil level difference when the second gap B of the tapered roller bearing of the above embodiment was changed in the experiment shown in FIG. Note that FIG.
In the experiment, the number of rotations of the motor was 2500 rpm.
In the above embodiment, the second gap B is set to 1.5 mm so that the oil level difference has a maximum value. As shown in FIG. 5B, if the second gap B is set to 1.5 mm, the inner diameter Y1 of the flange 6 of the retainer 5 is equal to the center of the revolving circle at the center of the small diameter end face 15 of the tapered roller 3. It is smaller than the diameter Y2. When the second gap B is set to be larger than 1.5 mm and set as shown in FIG. 5C, the amount of lubricating oil sucked from the second gap B decreases from the maximum value. Also,
Even when the second gap B is smaller than 1.5 mm and is set as shown in FIG. 5A, the amount of lubricating oil sucked from the second gap B decreases from the maximum value. It has been experimentally confirmed that this can be reproduced even when the number of rotations of the motor is changed.
【００３８】すなわち、この実施の形態によれば、第２
隙間Ｂを１.５ｍｍに設定して、円すいころ３の小径側
端面１５の中心の公転円の直径Ｙ２よりも上記保持器５
の鍔部６の内径側直径Ｙ１を小さく設定したことで、ポ
ンプ作用を極大にすることができたのである。That is, according to this embodiment, the second
The gap B is set to 1.5 mm, and the retainer 5 is larger than the diameter Y2 of the revolving circle at the center of the small-diameter side end face 15 of the tapered roller 3.
By setting the inner diameter Y1 of the flange 6 small, the pumping action could be maximized.
【００３９】尚、上記実施形態では、保持器５の小径側
端部を鍔部６で構成したが、上記小径側端部を厚肉部で
構成してもよい。In the above embodiment, the small-diameter end of the retainer 5 is formed by the flange 6, but the small-diameter end may be formed by a thick portion.
【００４０】[0040]
【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、保持器の大径側端部と上記内輪
の大径側端部との間の第１隙間Ｄが、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、上記第２隙間Ｂが、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３隙間Ａよりも大き
く、上記第３隙間Ａを、上記保持器が上記外輪に接触し
ない範囲で保持器が外輪に近接するような値に設定した
ものである。As is clear from the above, in the tapered roller bearing according to the first aspect of the present invention, the first gap D between the large-diameter end of the retainer and the large-diameter end of the inner ring is defined as follows. The second gap B is larger than the second gap B between the small diameter end of the cage and the small diameter end of the inner ring, and the second gap B is smaller than the small diameter end of the cage and the small diameter end of the outer ring. The third gap A is set to a value larger than the third gap A between the outer ring and the third gap A such that the cage approaches the outer ring within a range where the cage does not contact the outer ring.
【００４１】この請求項１の発明によれば、回転時に潤
滑油が排出される第１隙間Ｄを、回転時に潤滑油が吸入
される第２隙間Ｂよりも大きくしたから、第２隙間Ｂか
ら吸入した潤滑油をスムーズに第１隙間Ｄから排出させ
ることができ、したがって、潤滑油の流れを円滑にし
て、潤滑性能を向上させることができる。According to the first aspect of the present invention, the first gap D from which the lubricating oil is discharged during rotation is made larger than the second gap B from which the lubricating oil is sucked during rotation. The sucked lubricating oil can be smoothly discharged from the first gap D, so that the flow of the lubricating oil can be made smooth and the lubricating performance can be improved.
【００４２】また、潤滑油が吸入される小径側の第２隙
間Ｂを、同じ小径側にあって潤滑油が排出される第３隙
間Ａよりも大きくしたから、円すいころを通過せずに第
２隙間Ｂから第３隙間Ａへ流れるの潤滑油の量を少なく
して、摺動部分への潤滑油供給量の増大を図れ、潤滑性
能の向上を図れる。Further, since the second gap B on the small diameter side where the lubricating oil is sucked is made larger than the third gap A on the same small diameter side where the lubricating oil is discharged, the second gap B without passing through the tapered rollers is formed. By reducing the amount of lubricating oil flowing from the second gap B to the third gap A, the amount of lubricating oil supplied to the sliding portion can be increased, and the lubrication performance can be improved.
【００４３】また、上記第３隙間Ａを保持器と外輪とが
接触せずに近接するような値にしたから、第２隙間Ｂか
ら吸入された潤滑油が円すいころを素通りして第３隙間
Ａから排出されてしまうことを防げる。したがって、第
２隙間Ｂから吸入した潤滑油を最大限に軸受の摺動部分
に導入でき、潤滑性能の向上を図れる。Further, since the third gap A is set to a value such that the cage and the outer ring are close to each other without making contact with each other, the lubricating oil sucked from the second gap B passes through the tapered rollers and passes through the third gap A. A can be prevented from being discharged from A. Therefore, the lubricating oil sucked from the second gap B can be introduced to the sliding portion of the bearing to the maximum, and the lubrication performance can be improved.
【００４４】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、上記第３隙間Ａが０.１乃
至０.５ｍｍに設定されている。According to a second aspect of the present invention, in the tapered roller bearing according to the first aspect, the third gap A is set to 0.1 to 0.5 mm.
【００４５】この請求項２の発明によれば、回転の保持
器と外輪との接触を防ぎつつ、上記第３隙間Ａから潤滑
油が排出されることを最大限に抑制して、潤滑に寄与し
ない第２隙間Ｂから第３隙間Ａへの潤滑油の流れを最小
にできる。したがって、潤滑性能の向上を図れる。According to the second aspect of the present invention, the contact between the rotating cage and the outer ring is prevented, and at the same time, the discharge of the lubricating oil from the third gap A is suppressed to the maximum, thereby contributing to lubrication. The flow of the lubricating oil from the second gap B to the third gap A, which is not performed, can be minimized. Therefore, the lubrication performance can be improved.
【００４６】また、請求項３の発明によれば、請求項１
または２に記載の円すいころ軸受において、上記円すい
ころの小径側端面の中心の公転円の直径よりも、上記保
持器の小径側端部の内径側直径が小さくなるように設定
されている。According to the invention of claim 3, according to claim 1,
Alternatively, in the tapered roller bearing described in 2, the diameter of the inner diameter side of the small diameter side end of the retainer is set to be smaller than the diameter of the revolving circle at the center of the small diameter side end face of the tapered roller.
【００４７】発明者らは、保持器の小径側端部の内径側
直径を円すいころの小径側端部中心の公転円直径よりも
小さく設定したときに、第２隙間Ｂから吸入される潤滑
油量が極大値を示すことを実験で確認することができた
から、請求項３の発明によれば、第２隙間Ｂの広げ過ぎ
による潤滑油吸入量の減少を抑えることができ、潤滑性
能の向上を図れる。When the inventors set the inner diameter of the small-diameter end of the cage to be smaller than the revolving circle diameter at the center of the small-diameter end of the tapered roller, the lubricating oil sucked from the second gap B is set. Since it was confirmed by experiments that the amount showed a maximum value, according to the invention of claim 3, a decrease in the amount of lubricating oil sucked due to the second gap B being excessively widened can be suppressed, and the lubrication performance can be improved. Can be achieved.
【図面の簡単な説明】[Brief description of the drawings]
【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】 上記実施形態および比較対象例の潤滑油流れ
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 the flow of a lubricating oil in the embodiment and a comparative example.
【図３】 第２隙間Ｂの所定値において油面差が極大値
を示すことを確認した実験結果を示す特性図である。FIG. 3 is a characteristic diagram showing an experimental result of confirming that a difference in oil level shows a maximum value at a predetermined value of a second gap B.
【図４】 上記潤滑油流れ確認実験結果から判明した各
第３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. 4 is a schematic diagram showing the direction of the flow of the lubricating oil in each of the third gaps A, B, C, and D found from the results of the lubricating oil flow confirmation experiment.
【図５】 図５(Ａ)は上記実施形態よりも第２隙間Ｂが
小さく設定された様子を示す模式図であり、図５(Ｂ)は
上記実施形態と同様に第２隙間Ｂ＝１.５ｍｍに設定さ
れた様子を示す模式図であり、図５(Ｃ)は上記実施形態
よりも第２隙間Ｂが大きく設定された様子を示す模式図
である。FIG. 5A is a schematic diagram showing a state in which a second gap B is set smaller than that in the above embodiment, and FIG. 5B is a diagram showing a second gap B = 1 as in the above embodiment. FIG. 5C is a schematic diagram illustrating a state where the second gap B is set to be larger than that of the above-described embodiment.
【図６】 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. 6 is a cross-sectional view of a main part showing an experimental apparatus for the lubricating oil flow confirmation experiment.
【図７】 従来の円すいころ軸受の要部断面図である。FIG. 7 is a sectional view of a main part of a conventional tapered roller bearing.
１…内輪、２…外輪、３…円すいころ、５…保持器、５
ａ…窓、６…鍔部、７…小径側鍔、８…大径側鍔、１
０,１１…軌道面、１２…大径側端部、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: flange, 7: small-diameter flange, 8: large-diameter flange, 1
0,11: Track surface, 12: Large diameter end, 13: Small diameter end, 15: Small diameter end, 17: Large diameter end, 20: Tapered roller bearing, A, B, C, D ... Gap.
Claims (3)
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、 上記保持器の大径側端部と上記内輪の大径側端部との間
の第１隙間Ｄが、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、上記第２
隙間Ｂが、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３隙間Ａよりも大きく、 上記第３隙間Ａを、上記保持器が上記外輪に接触しない
範囲で保持器が外輪に近接するような値に設定したこと
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 large-diameter end of the retainer and the inner ring are provided. The first gap D between the small diameter end of the cage and the second gap B between the small diameter end of the inner ring and the second gap B between the small diameter end of the inner ring and the second gap B is large.
The gap B is larger than the third gap A between the small-diameter end of the cage and the small-diameter end of the outer ring, and the third gap A is set so that the cage does not contact the outer ring. A tapered roller bearing characterized in that the retainer is set to a value close to the outer ring.
て、 上記第３隙間Ａが、０.１乃至０.５ｍｍに設定されてい
る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 the third gap A is set to 0.1 to 0.5 mm.
受において、 上記円すいころの小径側端面の中心の公転円の直径より
も、上記保持器のつばの内径側直径が小さいことを特徴
とする円すいころ軸受。3. The tapered roller bearing according to claim 1, wherein the diameter of the inner diameter side of the collar of the retainer is smaller than the diameter of the revolving circle at the center of the small diameter side end face of the tapered roller. Tapered roller bearings.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP24764296A JP4031073B2 (en) | 1996-09-19 | 1996-09-19 | Tapered roller bearing |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP24764296A JP4031073B2 (en) | 1996-09-19 | 1996-09-19 | Tapered roller bearing |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPH1089352A true JPH1089352A (en) | 1998-04-07 |
| JP4031073B2 JP4031073B2 (en) | 2008-01-09 |
Family
ID=17166539
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP24764296A Expired - Fee Related JP4031073B2 (en) | 1996-09-19 | 1996-09-19 | Tapered roller bearing |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JP4031073B2 (en) |
Cited By (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2006329257A (en) * | 2005-05-24 | 2006-12-07 | Jtekt Corp | Pinion shaft support device for vehicle |
| EP1693584A4 (en) * | 2003-11-07 | 2008-05-07 | Jtekt Corp | Oil lubrication-type rolling bearing device |
| WO2008149790A1 (en) * | 2007-06-06 | 2008-12-11 | Ntn Corporation | Taper 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 |
| EP1950434A4 (en) * | 2005-10-25 | 2010-03-03 | Ntn Toyo Bearing Co Ltd | TRONCONIC ROLLER BEARING |
| EP1785638A3 (en) * | 2005-11-15 | 2010-03-10 | JTEKT Corporation | Liquid lubricated tapered roller bearing device |
| EP1906036A3 (en) * | 2006-09-29 | 2010-03-24 | JTEKT Corporation | Tapered roller bearing and differential gear apparatus |
| EP2369190A1 (en) * | 2004-04-14 | 2011-09-28 | Jtekt Corporation | Tapered roller bearing |
| US9091300B2 (en) | 2013-03-06 | 2015-07-28 | Aktiebolaget Skf | Rolling-element bearing |
-
1996
- 1996-09-19 JP JP24764296A patent/JP4031073B2/en not_active Expired - Fee Related
Cited By (12)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| EP1693584A4 (en) * | 2003-11-07 | 2008-05-07 | Jtekt Corp | Oil lubrication-type rolling bearing device |
| EP2369190A1 (en) * | 2004-04-14 | 2011-09-28 | Jtekt Corporation | 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 |
| JP2006329257A (en) * | 2005-05-24 | 2006-12-07 | Jtekt Corp | Pinion shaft support device for vehicle |
| EP1950434A4 (en) * | 2005-10-25 | 2010-03-03 | Ntn Toyo Bearing Co Ltd | TRONCONIC ROLLER BEARING |
| US7934873B2 (en) | 2005-10-25 | 2011-05-03 | Ntn Corporation | Tapered roller bearing |
| EP1785638A3 (en) * | 2005-11-15 | 2010-03-10 | JTEKT Corporation | Liquid lubricated tapered roller bearing device |
| US8876397B2 (en) | 2005-11-15 | 2014-11-04 | Jtekt Corporation | Liquid lubricating tapered roller bearing device |
| EP1906036A3 (en) * | 2006-09-29 | 2010-03-24 | JTEKT Corporation | Tapered roller bearing and differential gear apparatus |
| WO2008149790A1 (en) * | 2007-06-06 | 2008-12-11 | Ntn Corporation | Taper roller bearing |
| JP2008303942A (en) * | 2007-06-06 | 2008-12-18 | Ntn Corp | Tapered roller bearing |
| US9091300B2 (en) | 2013-03-06 | 2015-07-28 | Aktiebolaget Skf | Rolling-element bearing |
Also Published As
| Publication number | Publication date |
|---|---|
| JP4031073B2 (en) | 2008-01-09 |
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