JPS641710B2 - - Google Patents
Info
- Publication number
- JPS641710B2 JPS641710B2 JP59218061A JP21806184A JPS641710B2 JP S641710 B2 JPS641710 B2 JP S641710B2 JP 59218061 A JP59218061 A JP 59218061A JP 21806184 A JP21806184 A JP 21806184A JP S641710 B2 JPS641710 B2 JP S641710B2
- Authority
- JP
- Japan
- Prior art keywords
- oil
- bearing
- inner ring
- lubrication
- bearing inner
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Expired
Links
- 238000005461 lubrication Methods 0.000 claims description 50
- 238000001816 cooling Methods 0.000 claims description 27
- 238000000034 method Methods 0.000 claims description 11
- 230000002093 peripheral effect Effects 0.000 claims 1
- 239000003921 oil Substances 0.000 description 77
- 238000005096 rolling process Methods 0.000 description 8
- 239000010687 lubricating oil Substances 0.000 description 7
- 230000000052 comparative effect Effects 0.000 description 2
- 230000000694 effects Effects 0.000 description 2
- 238000002474 experimental method Methods 0.000 description 2
- 229910000831 Steel Inorganic materials 0.000 description 1
- 150000005690 diesters Chemical class 0.000 description 1
- 230000001050 lubricating effect Effects 0.000 description 1
- 239000000463 material Substances 0.000 description 1
- 238000005259 measurement Methods 0.000 description 1
- 230000000717 retained effect Effects 0.000 description 1
- 239000010959 steel 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
- F16C37/00—Cooling of bearings
- F16C37/007—Cooling of bearings of rolling bearings
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
- F16C33/30—Parts of ball or roller bearings
- F16C33/58—Raceways; Race rings
- F16C33/583—Details of specific parts of races
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- 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
- F16C33/6677—Details of supply of the liquid to the bearing, e.g. passages or nozzles from radial inside, e.g. via a passage through the shaft and/or inner ring
-
- 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
- F16C33/6681—Details of distribution or circulation inside the bearing, e.g. grooves on the cage or passages in the rolling elements
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
- F05B—INDEXING SCHEME RELATING TO WIND, SPRING, WEIGHT, INERTIA OR LIKE MOTORS, TO MACHINES OR ENGINES FOR LIQUIDS COVERED BY SUBCLASSES F03B, F03D AND F03G
- F05B2250/00—Geometry
- F05B2250/20—Geometry three-dimensional
- F05B2250/23—Geometry three-dimensional prismatic
- F05B2250/231—Geometry three-dimensional prismatic cylindrical
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C19/00—Bearings with rolling contact, for exclusively rotary movement
- F16C19/22—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings
- F16C19/24—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for radial load mainly
- F16C19/26—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for radial load mainly with a single row of rollers
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C2360/00—Engines or pumps
- F16C2360/23—Gas turbine engines
Description
【発明の詳細な説明】
産業上の利用分野
この発明は、ジエツト・エンジンのタービン、
圧縮機等の高速度回転体に使用される高速円筒こ
ろ軸受、特に、軸受内輪を冷却すると同時に、軸
受内に油を注ぎ込ませ、滑り部や転がり部に油を
供給するアンダー・レース潤滑法を用いた高速円
筒ころ軸受に関するものである。DETAILED DESCRIPTION OF THE INVENTION Field of Industrial Application This invention relates to a jet engine turbine,
High-speed cylindrical roller bearings used in high-speed rotating bodies such as compressors, especially the under-race lubrication method that cools the inner ring of the bearing and at the same time injects oil into the bearing to supply oil to the sliding and rolling parts. This article relates to the high-speed cylindrical roller bearings used.
従来の技術
ジエツト・エンジンのタービン、圧縮機等の高
速度回転体に使用される転がり軸受は、かなり過
酷な条件で運転される。その為に、軸受材料とし
て真空溶解した耐熱軸受鋼（Ｍ―50）が使われた
り、潤滑油としてジエステル油（MIL―Ｌ―
7808）或いはテトラエステル油（MIL―Ｌ―
23699）が使われたりしている。また、潤滑法に
もいろいろ研究がなされ、最近の高速回転用転が
り軸受には、アンダー・レース潤滑法が最適とさ
れ、一般に広く利用されている。このアンダー・
レース潤滑法は、軸受内輪を冷却すると同時に、
遠心力で軸受内に油を注ぎ込ませ、滑り部や転が
り部に油を供給する方法で、従来のジエツト潤滑
法に替るものである。BACKGROUND OF THE INVENTION Rolling bearings used in high-speed rotating bodies such as jet engine turbines and compressors are operated under fairly severe conditions. For this reason, vacuum-melted heat-resistant bearing steel (M-50) is used as the bearing material, and diester oil (MIL-L-
7808) or tetraester oil (MIL-L-
23699) is sometimes used. Various studies have also been conducted on lubrication methods, and the under-race lubrication method has been considered optimal for recent high-speed rolling bearings, and is generally widely used. This under-
The race lubrication method cools the inner ring of the bearing and at the same time
This method replaces the conventional jet lubrication method by injecting oil into the bearing using centrifugal force and supplying oil to sliding and rolling parts.
第５図及び第６図はアンダー・レース潤滑法を
用いた公知の高速円筒ころ軸受を示し、同図に於
いて、１は軸受内輪、２は軸受外輪、３は内外輪
１，２間に介在した転動体である円筒ころ、４は
円筒ころ３を回転自在に保持する保持器である。
そして、軸受内輪１の内周面には、多数の冷却溝
５が軸方向に設けられ、かつ、この冷却溝５と内
輪軌道面６の両ヌスミ部６ａ，６ｂとを夫々連通
する同径の潤滑路７ａ，７ｂが同じ個数ずつ設け
られている。 Figures 5 and 6 show a known high-speed cylindrical roller bearing using the under-race lubrication method. Cylindrical rollers 4, which are intervening rolling elements, are cages that rotatably hold the cylindrical rollers 3.
A large number of cooling grooves 5 are provided in the axial direction on the inner circumferential surface of the bearing inner ring 1, and the same-diameter cooling grooves 5 are provided in the axial direction to communicate the cooling grooves 5 with both the slotted portions 6a and 6b of the inner ring raceway surface 6, respectively. The same number of lubrication passages 7a and 7b are provided.
そして、前記高速円筒ころ軸受は、例えばジエ
ツト・エンジンのタービン、圧縮機等の高速度回
転体に組付けられおり、運転時、給油された油
を、軸受内輪１の冷却溝５に送り、冷却溝５を通
過させて軸受内輪１を冷却すると同時に、遠心力
で潤滑路７ａ，７ｂから軸受内に油を注ぎ込ま
せ、軸受内輪１と円筒ころ３の滑り部や転がり部
に油を供給して該部を潤滑するようになされてい
る。 The high-speed cylindrical roller bearing is assembled into a high-speed rotating body such as a jet engine turbine or compressor, and during operation, oil is sent to the cooling groove 5 of the inner ring 1 of the bearing for cooling. The bearing inner ring 1 is cooled by passing through the groove 5, and at the same time oil is poured into the bearing from the lubrication paths 7a and 7b by centrifugal force, and the oil is supplied to the sliding parts and rolling parts of the bearing inner ring 1 and the cylindrical rollers 3. It is designed to lubricate this part.
発明が解決しようとする問題点
ところで、この種の高速円筒ころ軸受は冷却用
油量と潤滑用油量が略同量で、かつ、軸受内輪１
の給油側潤滑路７ａと排油側潤滑路７ｂの潤滑用
油量が略同量であるのが望ましい。ところが、従
来の高速円筒ころ軸受では、給油側潤滑路７ａと
排油側潤滑路７ｂは同径であり、また、同数であ
るので、回転数が低い域では冷却用油量が潤滑用
油量より多いが、ある回転数以上になると、これ
が逆転し、潤滑用油量が冷却用油量より多くな
り、回転数の増加に伴い、その差が拡がつて行
く。これは、回転数が上がると、遠心力が増し、
この力が軸受内輪１の潤滑路７ａ，７ｂに油を送
り込んで潤滑用油量を多くしているからで、給油
量が少ないときの方が、多いときに比べ、冷却用
油量と潤滑用油量の逆転する点（冷却用油量と潤
滑用油量が同量になる点）が低い回転数になつて
行く傾向にある。従つて、高い回転数で良好な運
転条件を得るには、給油量を多くする必要があつ
た。また、上述のように給油量を多くして回転数
の高速度化を行つても、排油側の潤滑路７ｂを通
る油量が、給油側の潤滑路７ａを通る油量よりも
少なく、また、油の温度も給油側より排油側の油
温度の方が軸受内輪１を冷却した後だから高くな
り、軸受内輪１が歪んで円筒ころ３の端面摩耗等
の好ましくない現象が起こる。Problems to be Solved by the Invention Incidentally, in this type of high-speed cylindrical roller bearing, the amount of cooling oil and the amount of lubricating oil are approximately the same, and the bearing inner ring 1
It is desirable that the amounts of lubricating oil in the oil supply side lubrication path 7a and the oil discharge side lubrication path 7b are approximately the same amount. However, in conventional high-speed cylindrical roller bearings, the oil supply side lubrication passage 7a and the oil discharge side lubrication passage 7b have the same diameter and the same number, so the amount of cooling oil is equal to the amount of lubrication oil in the low rotation speed range. However, when the number of rotations exceeds a certain number, this is reversed, and the amount of lubricating oil becomes larger than the amount of cooling oil, and as the number of rotations increases, the difference widens. This is because as the rotation speed increases, centrifugal force increases,
This force feeds oil into the lubrication paths 7a and 7b of the bearing inner ring 1, increasing the amount of lubricating oil.When the amount of oil supplied is small, the amount of cooling oil and lubrication The point at which the oil amount reverses (the point where the amount of cooling oil and the amount of lubricating oil become the same amount) tends to move toward lower rotational speeds. Therefore, in order to obtain good operating conditions at high rotational speeds, it was necessary to increase the amount of oil supplied. Furthermore, even if the rotational speed is increased by increasing the amount of oil supplied as described above, the amount of oil passing through the lubrication path 7b on the oil drain side is smaller than the amount of oil passing through the lubrication path 7a on the oil supply side. Further, the oil temperature on the oil drain side is higher than that on the oil supply side because it is after the bearing inner ring 1 has been cooled, which causes undesirable phenomena such as distortion of the bearing inner ring 1 and end face wear of the cylindrical rollers 3.
これらの原因は、従来の高速円筒ころ軸受で
は、軸受内輪１の潤滑路７ａ，７ｂの孔径が、給
油側も排油側も同径で、しかも、その個数が同
じ、即ち、潤滑路７ａ，７ｂの総孔開口面積が同
じであるからと考えられる。 The reason for these problems is that in conventional high-speed cylindrical roller bearings, the lubrication passages 7a and 7b of the bearing inner ring 1 have the same diameter on both the oil supply side and the oil discharge side, and the number of lubrication passages 7a, 7b is the same. This is thought to be because the total hole opening area of 7b is the same.
問題点を解決するための手段
この発明は軸受内輪と、軸受外輪と、前記軸受
内外輪間に介在した円筒ころとからなり、前記軸
受内輪の内周面には、多数の冷却溝が軸方向に設
けられ、かつ、この冷却溝と内輪軌道面の両ヌス
ミ部とを夫々連通する潤滑路が数個ずつ設けられ
たアンダー・レース潤滑法を用いる高速円筒ころ
軸受に於いて、前記軸受内輪の冷却溝を給油側か
ら排油側に向けて漸次大きく形成し、かつ、給油
側潤滑路の総孔開口面積を排油側潤滑路の総孔開
口面積より小さく形成したものである。Means for Solving the Problems This invention consists of a bearing inner ring, a bearing outer ring, and cylindrical rollers interposed between the bearing inner and outer rings, and a large number of cooling grooves are formed in the axial direction on the inner circumferential surface of the bearing inner ring. In a high-speed cylindrical roller bearing using the under race lubrication method, in which several lubrication passages are provided, each communicating between the cooling groove and both hollow portions of the inner ring raceway surface, The cooling grooves are formed to gradually become larger from the oil supply side to the oil discharge side, and the total hole opening area of the oil supply side lubrication path is formed to be smaller than the total hole opening area of the oil discharge side lubrication path.
実施例
第１図及び第２図はこの発明に係る高速円筒こ
ろ軸受の一例を示し、同図に於いて、８は軸受内
輪、９は軸受外輪、１０は内外輪８，９間に介在
した転動体である円筒ころ、１１は円筒ころ１０
を回転自在に保持する保持器である。そして、軸
受内輪８の内周面には、多数の冷却溝１２が軸方
向に設けられ、かつ、この冷却溝１２と内輪軌道
面１３の両ヌスミ部１３ａ，１３ｂとを夫々連通
する潤滑路１４ａ，１４ｂが数個ずつ設けられて
いる。Embodiment Figures 1 and 2 show an example of a high-speed cylindrical roller bearing according to the present invention. Cylindrical rollers as rolling elements, 11 are cylindrical rollers 10
This is a retainer that rotatably holds the A large number of cooling grooves 12 are provided in the axial direction on the inner circumferential surface of the bearing inner ring 8, and lubrication passages 14a communicate between the cooling grooves 12 and the hollow portions 13a and 13b of the inner ring raceway surface 13, respectively. , 14b are provided.
上記構造の高速円筒ころ軸受に於いて、この発
明では排油側の圧力を給油側より低くして油が出
て行きやすいように軸受内輪８の冷却溝１２を給
油側から排油側に向けて漸次大きいテーパ状或い
はラツパ状に形成し、かつ、給油側潤滑路１４ａ
の総孔開口面積が排油側潤滑路１４ｂの総孔開口
面積より小さくなるように、給油側潤滑路１４ａ
を排油側潤滑路１４ｂより小さな孔径にするか、
或いはその個数を少なくしている。 In the high-speed cylindrical roller bearing of the above structure, the present invention directs the cooling groove 12 of the bearing inner ring 8 from the oil supply side to the oil drain side so that the pressure on the oil drain side is lower than that on the oil supply side so that oil can easily flow out. The oil supply side lubrication path 14a is formed into a tapered or turgid shape that gradually increases.
The oil supply side lubrication path 14a is arranged such that the total hole opening area of the oil supply side lubrication path 14a is smaller than the total hole opening area of the oil drain side lubrication path 14b.
Either make the hole diameter smaller than that of the oil drain side lubrication path 14b, or
Or the number is reduced.
そして、この発明の前記高速円筒ころ軸受は、
例えばジエツト・エンジンのタービン、圧縮機等
の高速度回転体に、第３図に示すように、組付け
られる。尚、同図に於いて、１５は回転軸、１６
はキヤツプ、１７はスリーブ、１８はハウジン
グ、１９は給油ノズルであつて、軸受内輪８が回
転軸１５上に嵌合されてキヤツプ１６により回転
軸１２上に固定したスリーブ１７に向けて押付け
て結合され、かつ、軸受外輪９がハウジング１８
に嵌合保持されている。そして、回転軸１５とキ
ヤツプ１６との間には給油通路２０が形成され、
また、スリーブ１７には排油通路２１が形成され
ており、運転時、給油ノズル１９より噴出された
油を、給油通路２０を経て軸受内輪８の冷却溝１
２に送り、冷却溝１２を通過させて軸受内輪８を
冷却すると同時に、遠心力等で潤滑路１４ａ，１
４ｂから軸受内に油を注ぎ込ませ、軸受内外輪
１，２、円筒ころ１０及び保持器１１の滑り部や
転がり部に油を供給して該部を潤滑するようにな
されている。 The high-speed cylindrical roller bearing of the present invention is
For example, it is assembled into a high-speed rotating body such as a jet engine turbine or compressor, as shown in FIG. In addition, in the same figure, 15 is a rotating shaft, 16
17 is a cap, 17 is a sleeve, 18 is a housing, and 19 is an oil supply nozzle, in which the bearing inner ring 8 is fitted onto the rotating shaft 15 and is pressed and coupled to the sleeve 17 fixed on the rotating shaft 12 by the cap 16. and the bearing outer ring 9 is attached to the housing 18.
It is mated and retained. A refueling passage 20 is formed between the rotating shaft 15 and the cap 16.
Further, an oil drain passage 21 is formed in the sleeve 17, and during operation, oil ejected from the oil supply nozzle 19 is passed through the oil supply passage 20 to the cooling groove 1 of the bearing inner ring 8.
2, the bearing inner ring 8 is cooled by passing through the cooling groove 12, and at the same time, the lubricating path 14a, 1 is cooled by centrifugal force or the like.
Oil is poured into the bearing from 4b, and is supplied to the sliding and rolling parts of the bearing inner and outer rings 1, 2, cylindrical rollers 10, and cage 11 to lubricate these parts.
第４図ａは給油側と排油側との潤滑路１４ａ，
１４ｂの総孔開口面積を同じにした場合、第４図
ｂは給油側潤滑路１４ａの総孔開口面積を排油側
潤滑路１４ｂの総孔開口面積より小さくした（実
験例では1/2にした）場合の油の分配状態の比較
実験を行つた結果を示すものである。この時の測
定は、給油量5.5／minで給油させ、無負荷の
状態で行つた。この実験結果から、給油側潤滑路
１４ａの総孔開口面積を排油側潤滑路１４ｂの総
孔開口面積の1/2にすることで、冷却用油量と潤
滑用油量との逆転点（冷却用油量と潤滑用油量と
が同一となる点）は、7600rpmから11000rpmへ
と高い回転数に移り、回転数の高速度化を推進す
ることが可能となる。このように冷却用油量と潤
滑用油量の逆転点が高い回転数に移るので、理想
的な軸受潤滑と軸受内輪８の冷却ができ、軸受内
輪８が歪んだり、クリープを起こしたり等の心配
がなくなる。 Figure 4a shows the lubrication path 14a between the oil supply side and the oil discharge side,
14b, the total hole opening area of the oil supply side lubrication path 14a is made smaller than the total hole opening area of the oil discharge side lubrication path 14b (in the experimental example, it is reduced to 1/2). This figure shows the results of a comparative experiment on the oil distribution state in the following cases. The measurements at this time were performed under no-load conditions with lubrication at a rate of 5.5/min. From this experimental result, by setting the total hole opening area of the oil supply side lubrication path 14a to 1/2 of the total hole opening area of the oil discharge side lubrication path 14b, it was found that the reversal point between the cooling oil amount and the lubrication oil amount ( At the point where the amount of cooling oil and the amount of lubricating oil are the same), the rotation speed shifts from 7,600 rpm to 11,000 rpm, making it possible to promote a higher rotation speed. In this way, the reversal point between the amount of cooling oil and the amount of lubricating oil moves to a higher rotational speed, so ideal bearing lubrication and cooling of the bearing inner ring 8 can be achieved, and the bearing inner ring 8 can be prevented from becoming distorted or creeping. No more worries.
以上のことから、アンダー・レース潤滑法を用
いた高速円筒ころ軸受に於いて給油側潤滑路１４
ａの総孔開口面積を排油側潤滑路１４ｂの総孔開
口面積より小さくする効果は十分にある。 From the above, in high-speed cylindrical roller bearings using the under race lubrication method, the oil supply side lubrication path 14
There is a sufficient effect of making the total hole opening area of a smaller than the total hole opening area of the drain oil side lubrication path 14b.
発明の効果
この発明は、以上説明したように、アンダー・
レース潤滑法を用いた高速円筒ころ軸受に於い
て、軸受内輪の冷却溝を給油側から排油側に向か
つて漸次大きいテーパ状或いはラツパ状に形成
し、かつ、給油側潤滑路の総孔開口面積を排油側
潤滑路の総孔開口面積より小さくしたもので、回
転数の高速度化を推進することができ、しかも排
油側に油が流れ易くなつて排油側と給油側の潤滑
路の油量が略同量になるので、軸受内輪が歪んで
円筒ころの端面摩耗等の心配がなくなり、軸受寿
命の向上が図れる。Effects of the Invention As explained above, this invention provides under-
In high-speed cylindrical roller bearings using the race lubrication method, the cooling groove in the inner ring of the bearing is formed in a tapered or tapered shape that gradually increases from the oil supply side to the oil drain side, and the total hole opening of the oil supply side lubrication path is The area is smaller than the total hole opening area of the lubrication path on the oil drain side, which allows for higher rotation speeds, and also allows oil to flow more easily to the oil drain side, improving lubrication between the oil drain side and the oil supply side. Since the amount of oil in the passage is approximately the same, there is no need to worry about distortion of the bearing inner ring and end face wear of the cylindrical rollers, and the life of the bearing can be improved.
第１図及び第２図はこの発明の高速円筒ころ軸
受の正面図及び第１図のＡ―Ａ線縦断面図、第３
図はこの発明の高速円筒ころ軸受を高速回転体に
組み込んだ要部拡大断面図、第４図ａおよびｂは
従来品と本発明品との比較実験結果を示すグラ
フ、第５図及び第６図は従来の高速円筒ころ軸受
の正面図及び第５図のＢ―Ｂ線縦断面図である。
８…軸受内輪、９…軸受外輪、１０…円筒こ
ろ、１１…保持器、１２…冷却溝、１３…内輪軌
道面、１４ａ…給油側潤滑路、１４ｂ…排油側潤
滑路。
1 and 2 are a front view of a high-speed cylindrical roller bearing of the present invention, a vertical sectional view taken along the line A--A in FIG.
The figure is an enlarged sectional view of the main parts of the high-speed cylindrical roller bearing of the present invention incorporated into a high-speed rotating body, Figures 4a and b are graphs showing the results of comparative experiments between the conventional product and the product of the present invention, and Figures 5 and 6 are The figures are a front view of a conventional high-speed cylindrical roller bearing and a longitudinal sectional view taken along the line BB in FIG. 8... Bearing inner ring, 9... Bearing outer ring, 10... Cylindrical roller, 11... Cage, 12... Cooling groove, 13... Inner ring raceway surface, 14a... Oil supply side lubrication path, 14b... Oil discharge side lubrication path.
Claims (1)
に介在した円筒ころとからなり、前記軸受内輪の
内周面には、多数の冷却溝が軸方向に設けられ、
かつ、この冷却溝と内輪軌道面の両ヌスミ部とを
夫々連通する潤滑路が数個ずつ設けられたアンダ
ー・レース潤滑法を用いる高速円筒ころ軸受に於
いて、前記軸受内輪の冷却溝を給油側から排油側
に向けて漸次大きく形成し、かつ、給油側潤滑路
の総孔開口面積を排油側潤滑路の総孔開口面積よ
り小さく形成したことを特徴とする高速円筒ころ
軸受。1 Consisting of a bearing inner ring, a bearing outer ring, and cylindrical rollers interposed between the bearing inner and outer rings, and a large number of cooling grooves are provided in the axial direction on the inner peripheral surface of the bearing inner ring,
In a high-speed cylindrical roller bearing using an under-race lubrication method in which several lubrication passages are provided that communicate the cooling groove with both grooved portions of the inner ring raceway surface, the cooling groove of the bearing inner ring is lubricated. 1. A high-speed cylindrical roller bearing characterized in that the holes are formed gradually larger from the side toward the oil drain side, and the total hole opening area of the oil supply side lubrication path is smaller than the total hole opening area of the oil drain side lubrication path.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP59218061A JPS6196219A (en) | 1984-10-16 | 1984-10-16 | High speed cylindrical roller bearing |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP59218061A JPS6196219A (en) | 1984-10-16 | 1984-10-16 | High speed cylindrical roller bearing |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS6196219A JPS6196219A (en) | 1986-05-14 |
| JPS641710B2 true JPS641710B2 (en) | 1989-01-12 |
Family
ID=16714031
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP59218061A Granted JPS6196219A (en) | 1984-10-16 | 1984-10-16 | High speed cylindrical roller bearing |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS6196219A (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2011106593A (en) * | 2009-11-18 | 2011-06-02 | Mitsubishi Heavy Industries Food & Packaging Machinery Co Ltd | Dew condensation preventing device for bearing of rotary joint |
Families Citing this family (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| FR2878589B1 (en) * | 2004-11-29 | 2008-06-13 | Snecma Moteurs Sa | LUBRICANT UNDER-FEEDING COMPENSATION IN INTER-TREE BEARING |
| GB2421054A (en) * | 2004-12-08 | 2006-06-14 | Boc Group Plc | Vacuum pump with cooled shaft seal surface and bearing |
| US20070086688A1 (en) * | 2005-10-17 | 2007-04-19 | Rexnord Industries, Llc | Vented bearing assembly |
| JP5598075B2 (en) * | 2010-04-28 | 2014-10-01 | 株式会社ジェイテクト | Rolling bearing device |
| EP3586022B1 (en) | 2017-02-22 | 2021-04-07 | Volvo Truck Corporation | A bearing arrangement and an assembly comprising such bearing arrangement |
| CN108488236A (en) * | 2018-05-17 | 2018-09-04 | 中国航发哈尔滨轴承有限公司 | The cylinder roller bearing and mating clamp nut of a kind of lubrication system |
-
1984
- 1984-10-16 JP JP59218061A patent/JPS6196219A/en active Granted
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2011106593A (en) * | 2009-11-18 | 2011-06-02 | Mitsubishi Heavy Industries Food & Packaging Machinery Co Ltd | Dew condensation preventing device for bearing of rotary joint |
Also Published As
| Publication number | Publication date |
|---|---|
| JPS6196219A (en) | 1986-05-14 |
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