JP2002054451A - Rotary support device for turbo-charger - Google Patents
Rotary support device for turbo-chargerInfo
- Publication number
- JP2002054451A JP2002054451A JP2000241988A JP2000241988A JP2002054451A JP 2002054451 A JP2002054451 A JP 2002054451A JP 2000241988 A JP2000241988 A JP 2000241988A JP 2000241988 A JP2000241988 A JP 2000241988A JP 2002054451 A JP2002054451 A JP 2002054451A
- Authority
- JP
- Japan
- Prior art keywords
- peripheral surface
- outer peripheral
- turbocharger
- outer ring
- ball bearing
- 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.)
- Withdrawn
Links
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
- F16C33/30—Parts of ball or roller bearings
- F16C33/66—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
-
- 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
- F16C19/02—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows
- F16C19/14—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load
- F16C19/16—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with a single row of balls
- F16C19/163—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with a single row of balls with angular contact
-
- 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
- F16C19/54—Systems consisting of a plurality of bearings with rolling friction
- F16C19/546—Systems with spaced apart rolling bearings including at least one angular contact bearing
- F16C19/547—Systems with spaced apart rolling bearings including at least one angular contact bearing with two angular contact rolling bearings
- F16C19/548—Systems with spaced apart rolling bearings including at least one angular contact bearing with two angular contact rolling bearings in O-arrangement
-
- 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
- F16C2360/24—Turbochargers
Abstract
Description
【０００１】[0001]
【発明の属する技術分野】本発明のターボチャージャ用
回転支持装置は、例えば自動車用エンジンの出力を向上
させる為のターボチャージャに組み込み、インペラとタ
ービンとを接続する回転軸を軸受ハウジングに対し、回
転自在に支持する為に利用する。BACKGROUND OF THE INVENTION A rotary support device for a turbocharger according to the present invention is incorporated in a turbocharger for improving the output of an automobile engine, for example, and a rotary shaft connecting an impeller and a turbine is rotated with respect to a bearing housing. Use to support freely.
【０００２】[0002]
【従来の技術】エンジンの出力を排気量を変えずに増大
させる為、エンジンに送り込む空気を排気のエネルギに
より圧縮するターボチャージャが、広く使用されてい
る。このターボチャージャは、排気のエネルギを、排気
通路の途中に設けたタービンにより回収し、このタービ
ンをその端部に固定した回転軸により、給気通路の途中
に設けたコンプレッサのインペラを回転させる。このイ
ンペラは、エンジンの運転に伴って数万乃至は十数万mi
n-1 （r.p.m.）の速度で回転し、上記給気通路を通じて
エンジンに送り込まれる空気を圧縮する。2. Description of the Related Art In order to increase the output of an engine without changing the displacement, a turbocharger for compressing air sent to the engine by the energy of the exhaust is widely used. This turbocharger collects the energy of exhaust gas by a turbine provided in the middle of the exhaust passage, and rotates an impeller of a compressor provided in the middle of the air supply passage by a rotating shaft fixed to an end of the turbine. This impeller is tens of thousands or hundreds of thousands
It rotates at a speed of n -1 (rpm) and compresses the air sent to the engine through the air supply passage.
【０００３】図２〜３は、この様なターボチャージャの
１例を示している。このターボチャージャは、排気流路
１を流通する排気により、回転軸２の一端（図２の右
端）に固定したタービン３を回転させる。この回転軸２
の回転は、この回転軸２の他端（図２の左端）に固定し
たインペラ４に伝わり、このインペラ４が給気流路５内
で回転する。この結果、この給気流路５の上流端開口か
ら吸引された空気が圧縮されて、ガソリン、軽油等の燃
料と共にエンジンのシリンダ室内に送り込まれる。この
様なターボチャージャの回転軸２は、数万〜十数万min
-1 （r.p.m.）もの高速で回転し、しかも、エンジンの
運転状況に応じてその回転速度が頻繁に変化する。従っ
て、上記回転軸２は、軸受ハウジング６に対し、小さな
回転抵抗で支持し、しかも回転支持部の潤滑を十分に考
慮する必要がある。FIGS. 2 and 3 show an example of such a turbocharger. The turbocharger rotates the turbine 3 fixed to one end (the right end in FIG. 2) of the rotating shaft 2 by exhaust gas flowing through the exhaust passage 1. This rotating shaft 2
Is transmitted to the impeller 4 fixed to the other end (the left end in FIG. 2) of the rotating shaft 2, and the impeller 4 rotates in the air supply flow path 5. As a result, the air sucked from the upstream end opening of the air supply passage 5 is compressed and sent into the cylinder chamber of the engine together with fuel such as gasoline or light oil. The rotation axis 2 of such a turbocharger is tens of thousands to several hundred thousand minutes.
It rotates at a speed as high as -1 (rpm), and its rotation speed changes frequently depending on the operating condition of the engine. Therefore, it is necessary to support the rotating shaft 2 with a small rotation resistance to the bearing housing 6 and to sufficiently consider the lubrication of the rotation supporting portion.
【０００４】この為に従来から、上記軸受ハウジング６
の内側に上記回転軸２を第一、第二の玉軸受７、８によ
り、回転自在に支持している。これら第一、第二の玉軸
受７、８はそれぞれ、図４に示す様なアンギュラ型玉軸
受である。これら第一、第二の玉軸受７、８の構成は、
基本的には同じである。但し、これら両玉軸受７、８の
うち、高温の排気が流通する排気流路１に近く、温度上
昇が著しい第一の玉軸受７の潤滑条件は、低温の空気が
流通する給気流路５に近く、温度上昇がそれ程著しくは
ない、第二の玉軸受８に比べて厳しくなる。この為、上
記第一の玉軸受７の潤滑を十分に行なって、この第一の
玉軸受７に焼き付き等の損傷が発生するのを防止してい
る。本発明は、この様な第一の玉軸受７の潤滑性能の向
上を図るものである。就いては、以下の説明は、この第
一の玉軸受７を中心に行なう。For this reason, conventionally, the bearing housing 6
The above-mentioned rotary shaft 2 is rotatably supported by first and second ball bearings 7 and 8 on the inside. Each of these first and second ball bearings 7 and 8 is an angular type ball bearing as shown in FIG. The configuration of these first and second ball bearings 7, 8 is as follows.
Basically the same. However, of these two ball bearings 7, 8, the lubrication condition of the first ball bearing 7, which is close to the exhaust passage 1 through which high-temperature exhaust flows and whose temperature rises remarkably, is determined by the air supply passage 5 through which low-temperature air flows. And the temperature rise is not so remarkable, it becomes more severe than the second ball bearing 8. Therefore, the first ball bearing 7 is sufficiently lubricated to prevent the first ball bearing 7 from being damaged such as seizure. The present invention aims to improve the lubrication performance of the first ball bearing 7 as described above. Therefore, the following description will focus on the first ball bearing 7.
【０００５】この第一の玉軸受７は、内周面に外輪軌道
９を有する外輪１０と、外周面に内輪軌道１１を有する
内輪１２と、これら外輪軌道９と内輪軌道１１との間に
転動自在に設けた複数個の玉１３、１３とを備える。
又、これら各玉１３、１３は、円環状の保持器１４に設
けた複数のポケット１５内に、それぞれ１個ずつ転動自
在に保持している。又、図示の例の場合には、上記内輪
１２を、片側の肩部をなくした、所謂カウンタボアとし
ている。又、上記保持器１４の外周面を、上記外輪１０
の内周面に近接対向させる事により、この保持器１４の
直径方向位置をこの外輪１０により規制する、外輪案内
としている。The first ball bearing 7 has an outer race 10 having an outer raceway 9 on an inner peripheral surface, an inner race 12 having an inner raceway 11 on an outer peripheral surface, and a rolling contact between the outer raceway 9 and the inner raceway 11. A plurality of balls 13, 13 movably provided.
Each of these balls 13 is held in a plurality of pockets 15 provided in an annular holder 14 so as to be able to roll one by one. In the illustrated example, the inner ring 12 has a so-called counter bore in which one shoulder is not provided. Further, the outer peripheral surface of the retainer 14 is
The outer ring guide restricts the diametrical position of the retainer 14 by the outer ring 10 by closely opposing the inner peripheral surface of the retainer 14.
【０００６】この様な第一の玉軸受７は、上記外輪１０
を前記軸受ハウジング６の一端部に内嵌すると共に、上
記内輪１２を上記回転軸２の一端部に外嵌固定する事に
より、この回転軸２の一端部を上記軸受ハウジング６に
対し、回転自在に支持している。又、上述した様に、同
様の構成を有する上記第二の玉軸受８は、外輪１０を軸
受ハウジング６の他端部に内嵌すると共に、内輪１２を
上記回転軸２の他端部に外嵌固定する事により、この回
転軸２の他端部を上記軸受ハウジング６に対し、回転自
在に支持している。又、上記第一、第二の玉軸受７、８
を構成する１対の外輪１０、１０には、圧縮ばね１６に
より互いに離れる方向の弾力を付与している。即ち、こ
れら両外輪１０、１０の互いに対向する端面にそれぞれ
押圧環１７、１７を突き合わせ、これら両押圧環１７、
１７同士の間に上記圧縮ばね１６を挟持している。従っ
て上記第一、第二の玉軸受７、８には、背面組み合わせ
（ＤＢ）型の接触角が付与された状態となる。[0006] Such a first ball bearing 7 is provided with the outer ring 10
Is internally fitted to one end of the bearing housing 6 and the inner ring 12 is externally fitted and fixed to one end of the rotary shaft 2 so that one end of the rotary shaft 2 is rotatable with respect to the bearing housing 6. I support it. As described above, in the second ball bearing 8 having the same configuration, the outer ring 10 is fitted inside the other end of the bearing housing 6 and the inner ring 12 is fitted outside the other end of the rotary shaft 2. The other end of the rotating shaft 2 is rotatably supported on the bearing housing 6 by being fitted and fixed. Also, the first and second ball bearings 7, 8
Are provided by a compression spring 16 with elasticity in a direction away from each other. That is, the pressing rings 17, 17 abut against the end faces of the outer rings 10, 10 facing each other, respectively.
The compression spring 16 is sandwiched between the members 17. Therefore, the first and second ball bearings 7 and 8 are provided with a back-to-back (DB) type contact angle.
【０００７】更に、上記軸受ハウジング６を納めたケー
シング１８内に給油通路を設けて、上記各玉軸受７、８
を潤滑自在としている。ターボチャージャを装着したエ
ンジンの運転時に潤滑油は、フィルタ１９により異物を
除去されてから、上記ケーシング１８の内周面と上記軸
受ハウジング６の外周面との間の隙間空間を通過して、
上記外輪１０に隣接する押圧環１７に設けたノズル孔２
０から、上記第一の玉軸受７を構成する内輪１２の外周
面に向け、径方向外方から斜めに噴出し、この第一の玉
軸受７を潤滑（オイルジェット潤滑）する。この様にし
て第一の玉軸受７に向けて噴出した潤滑油は、この第一
の玉軸受７の他、上記第二の玉軸受８も潤滑してから、
排油口２１から排出される。Further, an oil supply passage is provided in a casing 18 in which the bearing housing 6 is accommodated, and the respective ball bearings 7 and 8 are provided.
Is lubricated freely. During operation of the engine equipped with the turbocharger, the lubricating oil passes through a clearance space between the inner peripheral surface of the casing 18 and the outer peripheral surface of the bearing housing 6 after foreign substances are removed by the filter 19,
Nozzle hole 2 provided in pressing ring 17 adjacent to outer ring 10
From 0, the first ball bearing 7 is lubricated (oil jet lubrication) toward the outer peripheral surface of the inner ring 12 constituting the first ball bearing 7 obliquely from the outside in the radial direction. The lubricating oil jetted toward the first ball bearing 7 in this manner lubricates not only the first ball bearing 7 but also the second ball bearing 8,
The oil is discharged from the oil drain 21.
【０００８】[0008]
【発明が解決しようとする課題】上述した様な従来のタ
ーボチャージャ用回転支持装置の場合、ノズル孔２０か
ら噴出した潤滑油が、必ずしも第一の玉軸受７の潤滑の
為に有効に利用できない。即ち、上述した従来構造の場
合には、上記ノズル孔２０からこの第一の玉軸受７を構
成する内輪１２の端部外周面に向け噴出した潤滑油の多
くの部分が、高速で回転している、この内輪１２の外周
面に跳ね飛ばされて、上記第一の玉軸受７を潤滑する事
なく、周囲に飛散してしまう。In the case of the conventional turbocharger rotary support device as described above, the lubricating oil ejected from the nozzle hole 20 cannot always be used effectively for lubrication of the first ball bearing 7. . That is, in the case of the conventional structure described above, a large part of the lubricating oil that has been jetted from the nozzle hole 20 toward the outer peripheral surface of the end of the inner ring 12 constituting the first ball bearing 7 rotates at a high speed. The first ball bearing 7 is scattered around without being lubricated to the outer peripheral surface of the inner ring 12 without lubricating the first ball bearing 7.
【０００９】この結果、各玉１３、１３の転動面と、外
輪軌道９、内輪軌道１１、各ポケット１５の内面との、
転がり接触部又は滑り接触部に存在する潤滑油が不足す
る可能性がある。そして、不足した場合には、上記各ポ
ケット１５の内面等、各部の摩耗が著しくなり、ターボ
チャージャ用回転支持装置の耐久性が損なわれるだけで
なく、極端な場合には焼き付き等の損傷を発生する。特
に、互いに近接対向した状態で互いに高速で相対回転す
る、外輪１０の内周面と保持器１４の外周面との摺接部
の潤滑性確保が難しい。この為、この保持器１４に異常
摩耗や焼き付き等の損傷を発生する可能性がある。本発
明のターボチャージャ用回転支持装置は、この様な不都
合を解消すべく発明したものである。As a result, the rolling surfaces of the balls 13, 13 and the inner surfaces of the outer raceway 9, the inner raceway 11, and the pockets 15
There is a possibility that the lubricating oil existing in the rolling contact portion or the sliding contact portion is insufficient. If it is insufficient, wear of each part such as the inner surface of each pocket 15 becomes remarkable, and not only does the durability of the rotary support device for a turbocharger deteriorate, but in extreme cases, damage such as seizure occurs. I do. In particular, it is difficult to ensure the lubrication of the sliding contact portion between the inner peripheral surface of the outer race 10 and the outer peripheral surface of the retainer 14, which relatively rotate at a high speed in a state of being opposed to each other. For this reason, there is a possibility that the cage 14 may be damaged such as abnormal wear and seizure. The turbocharger rotation supporting device of the present invention has been invented in order to eliminate such inconvenience.
【００１０】[0010]
【課題を解決するための手段】本発明のターボチャージ
ャ用回転支持装置は、前述した従来から知られているタ
ーボチャージャ用回転支持装置と同様に、その一端部に
タービンを、その他端部にインペラを、それぞれ固定し
た回転軸を、軸受ハウジングの内側に回転自在に支持す
る為、これら回転軸の外周面と軸受ハウジングの内周面
との間に、外輪の内周面に形成した外輪軌道と内輪の外
周面に形成した内輪軌道との間に円環状の保持器により
保持された複数個の玉を転動自在に配置して成る玉軸受
を設けている。そして、この玉軸受を構成する上記保持
器の外周面と上記外輪の内周面とを近接対向させて、こ
の外輪によりこの保持器の径方向の位置決めを図ってい
る。The rotary support device for a turbocharger according to the present invention has a turbine at one end and an impeller at the other end, similarly to the above-described rotary support device for a turbocharger. In order to rotatably support the fixed rotating shafts inside the bearing housing, respectively, between the outer peripheral surface of these rotating shafts and the inner peripheral surface of the bearing housing, an outer ring raceway formed on the inner peripheral surface of the outer ring is provided. A ball bearing is provided in which a plurality of balls held by an annular cage are rollably arranged between an inner raceway formed on the outer peripheral surface of the inner race. The outer peripheral surface of the cage constituting the ball bearing and the inner peripheral surface of the outer ring are brought into close proximity to each other, and the outer ring is used to position the cage in the radial direction.
【００１１】特に、本発明のターボチャージャ用回転支
持装置に於いては、上記外輪の一部で上記各玉の転動面
と転がり接触しない部分に給油孔を形成し、この給油孔
から上記保持器の外周面に向け潤滑油を吐出自在として
いる。In particular, in the turbocharger rotation supporting device of the present invention, a lubrication hole is formed in a part of the outer race that does not come into rolling contact with the rolling surface of each ball, and the holding hole is formed from the lubrication hole. Lubricating oil can be discharged toward the outer peripheral surface of the container.
【００１２】[0012]
【作用】上述の様に構成する本発明のターボチャージャ
用回転支持装置の場合には、給油孔から吐出した潤滑油
の大部分が、互いに近接対向した状態で互いに高速で相
対回転する、外輪の内周面と保持器の外周面との摺接部
の潤滑に供される。この結果、上記給油孔から吐出した
潤滑油を、これら両周面同士の潤滑に有効利用して、玉
軸受の潤滑状態を良好にできる。In the case of the rotary support device for a turbocharger of the present invention configured as described above, most of the lubricating oil discharged from the oil supply hole rotates relatively at a high speed with respect to each other in a state of being opposed to each other. It is used for lubrication of the sliding contact portion between the inner peripheral surface and the outer peripheral surface of the cage. As a result, the lubricating oil discharged from the oil supply hole is effectively used for lubrication between the two peripheral surfaces, and the lubrication state of the ball bearing can be improved.
【００１３】[0013]
【発明の実施の形態】図１は、本発明の実施の形態の１
例を示している。尚、本発明の特徴は、ターボチャージ
ャ用回転支持装置に組み込む（前述の図２〜３に示した
第一の玉軸受７に相当する）玉軸受２２を構成する外輪
２３に給油孔２４を形成し、この給油孔２４から保持器
１４の外周面に潤滑油を吐出する事により、近接対向し
た状態で互いに高速で相対回転する、上記外輪２３の内
周面と上記保持器１４の外周面との間の潤滑状態を良好
にする点にある。上記ターボチャージャ用回転支持装置
の全体構成に就いては、前述の図２〜３に示した構造を
含み、従来から知られているものと同様であり、上記給
油孔２４に潤滑油を送り込む為の構造に就いても、図２
〜３に示した、ノズル孔２０の油を供給する為の給油通
路２５の一部を分岐して、上記外輪２３の外周面にまで
伸ばす事により、容易に実現できる。そこで、同等部分
に関する図示並びに説明は、省略若しくは簡略にし、以
下、本発明の特徴部分を中心に説明する。FIG. 1 shows a first embodiment of the present invention.
An example is shown. A feature of the present invention is that an oil supply hole 24 is formed in an outer ring 23 which constitutes a ball bearing 22 (corresponding to the above-described first ball bearing 7 shown in FIGS. 2 to 3) incorporated in a rotation support device for a turbocharger. By discharging lubricating oil from the oil supply hole 24 to the outer peripheral surface of the retainer 14, the inner peripheral surface of the outer race 23 and the outer peripheral surface of the retainer 14 rotate relatively at a high speed in a state of being close to each other. To improve the lubrication state during the period. The overall structure of the turbocharger rotation support device includes the structure shown in FIGS. 2 and 3 and is the same as conventionally known. Fig. 2
3 can be easily realized by branching a part of the oil supply passage 25 for supplying the oil of the nozzle hole 20 and extending to the outer peripheral surface of the outer ring 23. Therefore, illustration and description of equivalent parts are omitted or simplified, and the following description will focus on the characteristic parts of the present invention.
【００１４】上記外輪２３の片端部（図１の左端部）
で、各玉１３の転動面と転がり接触すべき外輪軌道９か
ら軸方向に外れた部分に上記給油孔２４を、上記外輪２
３の外周面と内周面とを連通させる状態で形成してい
る。この給油孔２４の上流端部である、上記外輪２３の
外周面側開口は、前述の図２〜３に示した給油通路２５
に通じさせている。従って上記給油孔２４には、フィル
タ１９（図２参照）を通過した潤滑油が、送り込み自在
である。そして、この様にして上記給油孔２４に送り込
まれた潤滑油は、この給油孔２４の下流端部である、上
記外輪２３の内周面側開口から、上記保持器１４の外周
面に向け吐出される。One end of the outer ring 23 (left end in FIG. 1)
The lubrication hole 24 is formed at a portion axially deviated from the outer raceway 9 to be in rolling contact with the rolling surface of each ball 13, and the outer race 2
3 is formed in a state where the outer peripheral surface and the inner peripheral surface communicate with each other. The opening on the outer peripheral surface side of the outer race 23, which is the upstream end of the oil supply hole 24, is connected to the oil supply passage 25 shown in FIGS.
Let me know. Therefore, the lubricating oil that has passed through the filter 19 (see FIG. 2) can be sent into the oil supply hole 24 freely. The lubricating oil thus fed into the oil supply hole 24 is discharged toward the outer peripheral surface of the retainer 14 from the inner peripheral surface side opening of the outer ring 23 at the downstream end of the oil supply hole 24. Is done.
【００１５】上述の様に構成する本発明のターボチャー
ジャ用回転支持装置の場合には、上記給油孔２４から吐
出した潤滑油の大部分が、互いに近接対向した状態で互
いに高速で相対回転する、上記外輪２３の内周面と上記
保持器１４の外周面との摺接部の潤滑に供される。この
結果、上記給油孔２４から吐出した潤滑油を、これら両
周面同士の潤滑に有効利用して、玉軸受２２の潤滑状態
を良好にできる。尚、本発明を実施する場合に、玉軸受
のうちで玉を設置した空間に潤滑油を噴出する為のノズ
ル孔２０（図２〜３）は必須ではないが、設ける事が好
ましい。In the case of the turbocharger rotation supporting device of the present invention configured as described above, most of the lubricating oil discharged from the oil supply hole 24 relatively rotates at a high speed in a state of being opposed to each other. It is used for lubrication of a sliding contact portion between the inner peripheral surface of the outer ring 23 and the outer peripheral surface of the cage 14. As a result, the lubricating oil discharged from the oil supply hole 24 is effectively used for lubrication between the two peripheral surfaces, and the lubrication state of the ball bearing 22 can be improved. In practicing the present invention, the nozzle hole 20 (FIGS. 2 and 3) for injecting the lubricating oil into the space where the ball is installed in the ball bearing is not essential, but is preferably provided.
【００１６】[0016]
【発明の効果】本発明のターボチャージャ用支持装置
は、以上に述べた通り構成し作用する為、使用条件が厳
しい玉軸受の潤滑性を良好にして、ターボチャージャの
耐久性及び信頼性の向上を図れる。Since the turbocharger support device of the present invention is constructed and operates as described above, the lubrication of ball bearings, which are used under severe conditions, is improved, and the durability and reliability of the turbocharger are improved. Can be achieved.
【図１】本発明の実施の形態の１例を示す、玉軸受の部
分断面図。FIG. 1 is a partial sectional view of a ball bearing showing an example of an embodiment of the present invention.
【図２】ターボチャージャの全体構成を示す断面図。FIG. 2 is a sectional view showing the overall configuration of the turbocharger.
【図３】ターボチャージャ用支持装置を示す、図２のＡ
部拡大図。FIG. 3A shows the turbocharger support device, FIG.
Part enlarged view.
【図４】従来のターボチャージャ用支持装置に組み込ん
でいた玉軸受の断面図。FIG. 4 is a sectional view of a ball bearing incorporated in a conventional turbocharger support device.
１ 排気流路 ２ 回転軸 ３ タービン ４ インペラ ５ 給気流路 ６ 軸受ハウジング ７ 第一の玉軸受 ８ 第二の玉軸受 ９ 外輪軌道 １０ 外輪 １１ 内輪軌道 １２ 内輪 １３ 玉 １４ 保持器 １５ ポケット １６ 圧縮ばね １７ 押圧環 １８ ケーシング １９ フィルタ ２０ ノズル孔 ２１ 排油口 ２２ 玉軸受 ２３ 外輪 ２４ 給油孔 ２５ 給油通路 DESCRIPTION OF SYMBOLS 1 Exhaust flow path 2 Rotary shaft 3 Turbine 4 Impeller 5 Air supply flow path 6 Bearing housing 7 First ball bearing 8 Second ball bearing 9 Outer ring raceway 10 Outer ring 11 Inner ring raceway 12 Inner ring 13 Ball 14 Cage 15 Pocket 16 Compression spring 17 Pressing ring 18 Casing 19 Filter 20 Nozzle hole 21 Oil discharge port 22 Ball bearing 23 Outer ring 24 Oil supply hole 25 Oil supply passage
───────────────────────────────────────────────────── フロントページの続き (72)発明者 池田 憲文 神奈川県藤沢市鵠沼神明一丁目５番50号 日本精工株式会社内 Ｆターム(参考） 3G005 FA13 FA31 GB55 JA40 3J101 AA02 AA32 AA42 AA54 AA62 BA54 BA56 CA08 CA13 EA67 FA32 GA01 GA26 ────────────────────────────────────────────────── ─── Continuation of the front page (72) Inventor Norifumi Ikeda 1-5-150 Kugenuma Shinmei, Fujisawa-shi, Kanagawa F-term in NSK Ltd. (reference) 3G005 FA13 FA31 GB55 JA40 3J101 AA02 AA32 AA42 AA54 AA62 BA54 BA56 CA08 CA13 EA67 FA32 GA01 GA26
Claims (1)
インペラを、それぞれ固定した回転軸を、軸受ハウジン
グの内側に回転自在に支持する為、これら回転軸の外周
面と軸受ハウジングの内周面との間に、外輪の内周面に
形成した外輪軌道と内輪の外周面に形成した内輪軌道と
の間に円環状の保持器により保持された複数個の玉を転
動自在に配置して成る玉軸受を設け、この玉軸受を構成
する上記保持器の外周面と上記外輪の内周面とを近接対
向させて、この外輪によりこの保持器の径方向の位置決
めを図ったターボチャージャ用回転支持装置に於いて、
上記外輪の一部で上記各玉の転動面と転がり接触しない
部分に給油孔を形成し、この給油孔から上記保持器の外
周面に向け潤滑油を吐出自在とした事を特徴とするター
ボチャージャ用回転支持装置。A rotating shaft having a turbine fixed at one end and an impeller fixed at the other end is rotatably supported inside a bearing housing. Between the outer raceway formed on the inner peripheral surface of the outer race and the inner raceway formed on the outer peripheral surface of the inner race, a plurality of balls held by an annular retainer are arranged so as to roll freely. For a turbocharger in which the outer peripheral surface of the cage and the inner peripheral surface of the outer ring are closely opposed to each other, and the outer ring is used to position the cage in the radial direction. In the rotating support device,
A turbocharger, wherein a lubrication hole is formed in a part of the outer ring that does not come into rolling contact with the rolling surface of each ball, and lubricating oil is freely discharged from the lubrication hole toward the outer peripheral surface of the cage. Rotary support device for charger.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2000241988A JP2002054451A (en) | 2000-08-10 | 2000-08-10 | Rotary support device for turbo-charger |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2000241988A JP2002054451A (en) | 2000-08-10 | 2000-08-10 | Rotary support device for turbo-charger |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JP2002054451A true JP2002054451A (en) | 2002-02-20 |
Family
ID=18733083
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP2000241988A Withdrawn JP2002054451A (en) | 2000-08-10 | 2000-08-10 | Rotary support device for turbo-charger |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JP2002054451A (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2004316813A (en) * | 2003-04-17 | 2004-11-11 | Nsk Ltd | Roller bearing, roller bearing system and main shaft device for machine tool |
| US10670078B2 (en) * | 2016-08-03 | 2020-06-02 | Nsk Ltd. | Ball bearing and main shaft device for machine tool |
-
2000
- 2000-08-10 JP JP2000241988A patent/JP2002054451A/en not_active Withdrawn
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2004316813A (en) * | 2003-04-17 | 2004-11-11 | Nsk Ltd | Roller bearing, roller bearing system and main shaft device for machine tool |
| US10670078B2 (en) * | 2016-08-03 | 2020-06-02 | Nsk Ltd. | Ball bearing and main shaft device for machine tool |
| US10746227B2 (en) | 2016-08-03 | 2020-08-18 | Nsk Ltd. | Ball bearing and main shaft device for machine tool |
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Free format text: JAPANESE INTERMEDIATE CODE: A621 Effective date: 20050928 |
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