JP2014043919A - Rolling bearing device for turbocharger - Google Patents

Rolling bearing device for turbocharger Download PDF

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Publication number
JP2014043919A
JP2014043919A JP2012187487A JP2012187487A JP2014043919A JP 2014043919 A JP2014043919 A JP 2014043919A JP 2012187487 A JP2012187487 A JP 2012187487A JP 2012187487 A JP2012187487 A JP 2012187487A JP 2014043919 A JP2014043919 A JP 2014043919A
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Prior art keywords
bearing
turbocharger
rolling bearing
housing
bearing device
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JP2012187487A
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JP6079057B2 (en
Inventor
Takashi Iwata
孝 岩田
Chiaki Saito
千晃 齋藤
Yoshitaka Waseda
義孝 早稲田
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JTEKT Corp
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JTEKT Corp
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    • 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
    • F16C27/00—Elastic or yielding bearings or bearing supports, for exclusively rotary movement
    • F16C27/04—Ball or roller bearings, e.g. with resilient rolling bodies
    • F16C27/045—Ball or roller bearings, e.g. with resilient rolling bodies with a fluid film, e.g. squeeze film damping
    • 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
    • F16C2360/00—Engines or pumps
    • F16C2360/23—Gas turbine engines
    • F16C2360/24—Turbochargers
    • 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
    • F16C35/00—Rigid support of bearing units; Housings, e.g. caps, covers
    • F16C35/04—Rigid support of bearing units; Housings, e.g. caps, covers in the case of ball or roller bearings
    • F16C35/06—Mounting or dismounting of ball or roller bearings; Fixing them onto shaft or in housing
    • F16C35/07—Fixing them on the shaft or housing with interposition of an element
    • F16C35/077—Fixing them on the shaft or housing with interposition of an element between housing and outer race ring

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Rolling Contact Bearings (AREA)
  • Supercharger (AREA)
  • Support Of The Bearing (AREA)
  • Mounting Of Bearings Or Others (AREA)

Abstract

PROBLEM TO BE SOLVED: To provide a rolling bearing device for a turbocharger that is capable of reducing torque loss caused by agitation resistance of a lubricating oil in a rolling bearing.SOLUTION: A rolling bearing device for a turbocharger comprises a disc-like seal member 6 that is disposed at one end in an axial direction of a bearing housing 10 to seal an opening 7a of an interior space 7 of a bearing. The seal member 6 comprises: a fixed portion 6a that is fixed to an axially outer end surface of an outer ring 22 and to an inner peripheral surface of an end of the bearing housing 10; and a disc portion 6b that extends from the fixed portion 6a toward an axis 50 of the bearing and is formed to overlap with an axially outer surface of an inner ring 21 in a radial direction. The disc portion 6b comprises: grooves 6d that are formed in opposite positions relative to an axial direction on an inner diameter side end of the opening 7a so as to allow an exterior space 9 of the housing located in the periphery of the bearing housing 10 to communicate with the interior space 7 of the bearing; and discharge holes 6c that are formed in opposite positions relative to the axial direction on an outer diameter side end of the opening 7a so as to allow the exterior space 9 of the housing to communicate with the interior space 7 of the bearing.

Description

本発明は、ターボチャージャー用転がり軸受装置に関する。   The present invention relates to a rolling bearing device for a turbocharger.

ターボチャージャーは、エンジンからの排気ガスによってタービンを回転させ、その回転によってコンプレッサを駆動し、エンジンへの吸気用の空気を圧縮する装置である。このようなターボチャージャーの回転軸は、転がり軸受により回転可能に支持されているが、回転数が非常に大きい（例えば毎分２０万回転）ので、転がり軸受を潤滑油により潤滑する必要がある。そこで、転がり軸受を保持する軸受ハウジングに給油孔を設けて潤滑油を流し込み、転がり軸受に給油する軸受装置がある。（例えば、特許文献１参照）   A turbocharger is a device that rotates a turbine by exhaust gas from an engine, drives a compressor by the rotation, and compresses air for intake to the engine. The rotating shaft of such a turbocharger is rotatably supported by a rolling bearing. However, since the rotational speed is very large (for example, 200,000 revolutions per minute), it is necessary to lubricate the rolling bearing with lubricating oil. In view of this, there is a bearing device in which an oil supply hole is provided in a bearing housing that holds a rolling bearing, lubricating oil is poured therein, and oil is supplied to the rolling bearing. (For example, see Patent Document 1)

このようなターボチャージャー用転がり軸受装置において、図７に示すように、軸受ハウジング１１０の両端部には、ターボチャージャーの回転軸１０３を回転可能に支持するタービン側の第１の転がり軸受１２０と、コンプレッサ側の第２の転がり軸受１３０とがそれぞれ配設される。
また、軸受ハウジング１１０には、軸受空間内の第１の転がり軸受１２０の近傍に位置する部分に、潤滑油を第１の転がり軸受１２０に向けて噴出するジェット給油孔（ノズル孔）１０９が形成されている。そして、ジェット給油孔１０９から噴出される潤滑油によって、第１の転がり軸受１２０が潤滑され、焼き付きが防止される。 In such a turbocharger rolling bearing device, as shown in FIG. 7, at both ends of the bearing housing 110, a first rolling bearing 120 on the turbine side that rotatably supports the rotating shaft 103 of the turbocharger, and A second rolling bearing 130 on the compressor side is provided.
Further, the bearing housing 110 is formed with a jet oil supply hole (nozzle hole) 109 for injecting lubricating oil toward the first rolling bearing 120 at a portion located in the vicinity of the first rolling bearing 120 in the bearing space. Has been. Then, the first rolling bearing 120 is lubricated by the lubricating oil ejected from the jet oil supply hole 109, and seizure is prevented.

特開２００９−２６４５２６号公報JP 2009-264526 A

ところで、前記した従来のターボチャージャー用転がり軸受装置においては、軸受ハウジング１１０のジェット給油孔１０９から第１の転がり軸受１２０に向けて潤滑油が直接的に噴出される構造上、例えば、エンジンが高回転域にあるときの状態において、ジェット給油孔１０９から第１の転がり軸受１２０に向けて噴出される潤滑油の噴出量が過大となることが想定される。この場合には、第１の転がり軸受１２０における潤滑油の攪拌抵抗によるトルク損失が大きくなる恐れがある。   By the way, the conventional turbocharger rolling bearing device described above has a structure in which the lubricating oil is directly ejected from the jet oil supply hole 109 of the bearing housing 110 toward the first rolling bearing 120. It is assumed that the amount of lubricating oil ejected from the jet oil supply hole 109 toward the first rolling bearing 120 becomes excessive in the state of being in the rotational region. In this case, torque loss due to the agitation resistance of the lubricating oil in the first rolling bearing 120 may increase.

この発明の目的は、前記問題点に鑑み、転がり軸受における潤滑油の攪拌抵抗によるトルク損失を軽減することができるターボチャージャー用転がり軸受装置を提供することである。   In view of the above problems, an object of the present invention is to provide a turbocharger rolling bearing device capable of reducing torque loss due to agitation resistance of lubricating oil in the rolling bearing.

前記課題を解決するために、この発明の請求項１に係るターボチャージャー用転がり軸受装置は、互いに軸方向に離れて配置され、ターボチャージャーの回転軸を回転自在に支持する一対の転がり軸受と、前記一対の軸受の外輪のそれぞれが軸方向の両端部内周面に嵌合される円筒状の軸受ハウジングと、を備え、前記軸受ハウジングは、前記ターボチャージャーの本体ケース内に装着され、前記軸受ハウジングの周囲と前記本体ケースの内周面との間の環状の隙間に潤滑油を満たしてオイルフィルムが形成され、前記転がり軸受には、その内外輪間に環状の軸受内部空間が形成され、前記潤滑油は、前記軸受ハウジングの周囲から前記軸受内部空間に流入して循環するターボチャージャー用転がり軸受装置であって、前記軸受ハウジングの軸方向の両端部又はいずれか一方の端部に配置され、前記軸受内部空間の開口部を塞ぐ円板状のシール部材をさらに備え、前記シール部材は、前記外輪の軸方向外側端面と前記軸受ハウジングの端部内周面との両方又はいずれか一方に固定される固定部と、この固定部から軸受の軸線に向かって延在し前記内輪の軸方向外側端面に径方向に重なって形成される円板部とを有し、前記円板部は、前記開口部の内径側端部に軸方向に対向する位置に形成され前記軸受ハウジングの周囲であるハウジング外部空間と前記軸受内部空間とを連通する流入部と、前記開口部の外径側端部に軸方向に対向する位置に形成され前記ハウジング外部空間と前記軸受内部空間とを連通する排出孔とを備えることを特徴とする。   In order to solve the above problems, a rolling bearing device for a turbocharger according to claim 1 of the present invention is a pair of rolling bearings that are arranged apart from each other in the axial direction and rotatably support the rotating shaft of the turbocharger. A cylindrical bearing housing in which outer rings of the pair of bearings are fitted to inner peripheral surfaces of both end portions in the axial direction, and the bearing housing is mounted in a main body case of the turbocharger, and the bearing housing An oil film is formed by filling an annular gap between the periphery of the body case and the inner peripheral surface of the main body case with lubricating oil, and an annular bearing inner space is formed between the inner and outer rings of the rolling bearing, Lubricating oil is a rolling bearing device for a turbocharger that circulates by flowing from the periphery of the bearing housing into the bearing internal space, A disc-shaped seal member that is disposed at both end portions or one of the end portions in the direction and closes the opening of the bearing internal space, and the seal member includes an axially outer end surface of the outer ring and the bearing housing. A fixed portion that is fixed to both or one of the inner peripheral surfaces of the end portion of the inner ring, and a circle that extends from the fixed portion toward the axis of the bearing and that overlaps the axially outer end surface of the inner ring in the radial direction. The disk portion is formed at a position facing the inner diameter side end portion of the opening portion in the axial direction, and communicates the housing outer space and the bearing inner space around the bearing housing. An inflow portion and a discharge hole formed in a position facing the outer diameter side end portion of the opening in the axial direction and communicating the housing outer space and the bearing inner space are provided.

請求項１のターボチャージャー用転がり軸受装置によれば、軸受ハウジングの周囲の潤滑油が、その軸方向の端部に固定されたシール部材により開口部から軸受内部空間への流入が制限される。また、このターボチャージャー用転がり軸受装置によれば、流入部から軸受内部空間に流入した潤滑油は、ターボチャージャーの回転軸が回転することにより、径方向外方へ移動して排出孔から排出されるので、転がり軸受における潤滑油の攪拌抵抗によるトルク損失を軽減することができる。   According to the rolling bearing device for a turbocharger of the first aspect, the lubricating oil around the bearing housing is restricted from flowing from the opening into the bearing internal space by the seal member fixed to the end portion in the axial direction. Further, according to this turbocharger rolling bearing device, the lubricating oil that has flowed into the bearing internal space from the inflow portion moves radially outward and is discharged from the discharge hole as the rotating shaft of the turbocharger rotates. Therefore, torque loss due to the stirring resistance of the lubricating oil in the rolling bearing can be reduced.

請求項２に係るターボチャージャー用転がり軸受装置は、前記排出孔は、その外接円径が前記外輪の内径以上に設定されて形成されることを特徴とする。   The rolling bearing device for a turbocharger according to claim 2 is characterized in that the discharge hole is formed so that a circumscribed circle diameter is set to be equal to or larger than an inner diameter of the outer ring.

請求項２のターボチャージャー用転がり軸受装置によれば、ターボチャージャーの回転軸が回転することにより、軸受内部空間の潤滑油が径方向外方へ移動して開口部の最外径端に対向して形成される排出孔から排出されるので、スムースに排出できて転がり軸受における潤滑油の攪拌抵抗によるトルク損失を軽減することができる。   According to the turbocharger rolling bearing device of the second aspect, when the rotating shaft of the turbocharger rotates, the lubricating oil in the inner space of the bearing moves radially outward to face the outermost diameter end of the opening. Since it is discharged from the discharge hole formed in this manner, it can be discharged smoothly, and torque loss due to the stirring resistance of the lubricating oil in the rolling bearing can be reduced.

請求項３に係るターボチャージャー用転がり軸受装置は、前記流入部は前記円板部の内径側が開口した溝又は孔形状の流入孔からなり、この溝又は流入孔の外接円径は、前記内輪の外径より大きく設定されることを特徴とする。   In the turbocharger rolling bearing device according to claim 3, the inflow portion is formed of a groove or a hole-shaped inflow hole opened on an inner diameter side of the disk portion, and a circumscribed circle diameter of the groove or the inflow hole is determined by the inner ring. It is characterized by being set larger than the outer diameter.

請求項３のターボチャージャー用転がり軸受装置によれば、開口部の最内径端に形成される溝又は流入孔から軸受内部空間に潤滑油が流入するので、潤滑油が不足しやすい内輪側が適正に潤滑される。また、このターボチャージャー用転がり軸受装置によれば、溝又は流入孔の大きさにより軸受内部空間への潤滑油の流入量を調整できる。   According to the rolling bearing device for a turbocharger of the third aspect, since the lubricating oil flows into the bearing inner space from the groove or inflow hole formed at the innermost end of the opening, the inner ring side where the lubricating oil tends to be insufficient is appropriately Lubricated. Further, according to this turbocharger rolling bearing device, the amount of lubricating oil flowing into the bearing internal space can be adjusted by the size of the groove or the inflow hole.

請求項４に係るターボチャージャー用転がり軸受装置は、前記流入部は前記円板部の内径端から帯状に全周に亘って形成され、前記流入部を除いた前記円板部の内径は、前記内輪の外径より大きく設定されることを特徴とする。   The rolling bearing device for a turbocharger according to claim 4, wherein the inflow portion is formed from the inner diameter end of the disc portion over the entire circumference in a band shape, and the inner diameter of the disc portion excluding the inflow portion is It is characterized by being set larger than the outer diameter of the inner ring.

請求項４のターボチャージャー用転がり軸受装置によれば、開口部の最内径端に形成される流入部から軸受内部空間に潤滑油が流入するので、潤滑油が不足しやすい内輪側が適正に潤滑される。また、このターボチャージャー用転がり軸受装置によれば、流入部の大きさにより軸受内部空間への潤滑油の流入量を調整できる。また、このターボチャージャー用転がり軸受装置によれば、帯状の流入部が円板部の全周に亘って形成されるので、周方向にバランス良く潤滑される。   According to the rolling bearing device for a turbocharger of the fourth aspect, since the lubricating oil flows into the bearing inner space from the inflow portion formed at the innermost end of the opening, the inner ring side where the lubricating oil tends to be insufficient is properly lubricated. The In addition, according to this turbocharger rolling bearing device, the amount of lubricating oil flowing into the bearing internal space can be adjusted by the size of the inflow portion. Further, according to this turbocharger rolling bearing device, the belt-like inflow portion is formed over the entire circumference of the disc portion, and therefore lubrication is performed with good balance in the circumferential direction.

請求項５に係るターボチャージャー用転がり軸受装置は、前記流入部及び前記排出孔は、互いに周方向に異なる位置に設けられることを特徴とする。   The rolling bearing device for a turbocharger according to a fifth aspect is characterized in that the inflow portion and the discharge hole are provided at different positions in the circumferential direction.

請求項５のターボチャージャー用転がり軸受装置によれば、軸受内部空間に流入した潤滑油が直ぐに排出することなく、潤滑した後に排出されるので、軸受内部が適正に潤滑される。   According to the rolling bearing device for a turbocharger of the fifth aspect, the lubricating oil that has flowed into the bearing internal space is discharged immediately after being lubricated without being immediately discharged, so that the inside of the bearing is properly lubricated.

本発明によれば、転がり軸受における潤滑油の攪拌抵抗によるトルク損失を軽減することができるターボチャージャー用転がり軸受装置を提供できる。   ADVANTAGE OF THE INVENTION According to this invention, the rolling bearing apparatus for turbochargers which can reduce the torque loss by the stirring resistance of the lubricating oil in a rolling bearing can be provided.

第１実施形態：本発明の一実施形態に係るターボチャージャー用転がり軸受装置を備えたターボチャージャーを示す断面図である。1st Embodiment: It is sectional drawing which shows the turbocharger provided with the rolling bearing apparatus for turbochargers which concerns on one Embodiment of this invention. 第１実施形態：図１のターボチャージャー用転がり軸受装置を拡大して示す断面図である。1st Embodiment: It is sectional drawing which expands and shows the rolling bearing apparatus for turbochargers of FIG. 第１実施形態：図２の要部拡大図である。1st Embodiment: It is the principal part enlarged view of FIG. 第１実施形態：図３のシール部材を矢印Ｙの方向から見た矢視図である。1st Embodiment: It is the arrow line view which looked at the sealing member of FIG. 第２実施形態：本発明の一実施形態に係るターボチャージャー用転がり軸受装置を備えたターボチャージャーの要部拡大断面図である。2nd Embodiment: It is a principal part expanded sectional view of the turbocharger provided with the rolling bearing device for turbochargers which concerns on one Embodiment of this invention. 第２実施形態：図５のシール部材を矢印Ｙ１の方向から見た矢視図である。2nd Embodiment: It is the arrow line view which looked at the sealing member of FIG. 5 from the direction of arrow Y1. 従来のターボチャージャー用転がり軸受装置を示す断面図である。It is sectional drawing which shows the conventional rolling bearing device for turbochargers.

以下、本発明のターボチャージャー用転がり軸受装置を具体化した実施形態について図面を参照しつつ説明する。   DESCRIPTION OF THE PREFERRED EMBODIMENTS Embodiments of a turbocharger rolling bearing device according to the present invention will be described below with reference to the drawings.

＜第１実施形態＞
図１は、本発明の一実施形態に係るターボチャージャー用転がり軸受装置１を備えたターボチャージャーＴを示す断面図である。ターボチャージャーＴは、排気流路４ａを流通する排気により、回転軸３の一端部（図１の右側）に固定されたタービンホイール４を回転させるようになっている。 <First Embodiment>
FIG. 1 is a cross-sectional view illustrating a turbocharger T including a turbocharger rolling bearing device 1 according to an embodiment of the present invention. The turbocharger T rotates the turbine wheel 4 fixed to one end portion (the right side in FIG. 1) of the rotating shaft 3 by the exhaust gas flowing through the exhaust passage 4a.

回転軸３の回転は、回転軸３の他端部（図１の左側）に固定されたコンプレッサインペラ５に伝わり、コンプレッサインペラ５が吸気流路５ａ内で回転する。この結果、吸気流路５ａの上流側開口から吸引された空気が圧縮され、これにより、ガソリンや軽油等の燃料と共に圧縮された空気が、図示しないエンジンのシリンダ室内に送り込まれる。   The rotation of the rotating shaft 3 is transmitted to the compressor impeller 5 fixed to the other end portion (left side in FIG. 1) of the rotating shaft 3, and the compressor impeller 5 rotates in the intake passage 5a. As a result, the air sucked from the upstream opening of the intake passage 5a is compressed, and the compressed air together with fuel such as gasoline or light oil is sent into a cylinder chamber of an engine (not shown).

ターボチャージャーＴの回転軸３は、数万〜十数万回転／分もの高速で回転し、しかも、エンジンの回転状況に応じて回転速度が頻繁に変化する。そのため、回転軸３は、その回転損失を低減すべくターボチャージャー用転がり軸受装置１によって、ターボチャージャーＴの本体ケース２に対して小さな回転抵抗で支持されている。具体的には、本体ケース２には、軸受ハウジング組付部２ａが形成され、軸受ハウジング組付部２ａの内周面には、ターボチャージャー用転がり軸受装置１が組み付けられる。ターボチャージャー用転がり軸受装置１は、タービンホイール４とコンプレッサインペラ５との間において回転軸３の軸方向中間部を回転自在に支持している。   The rotating shaft 3 of the turbocharger T rotates at a high speed of several tens of thousands to several ten thousand rotations / minute, and the rotation speed frequently changes according to the rotation state of the engine. Therefore, the rotating shaft 3 is supported by the turbocharger rolling bearing device 1 with a small rotational resistance with respect to the main body case 2 of the turbocharger T in order to reduce the rotation loss. Specifically, the main body case 2 is formed with a bearing housing assembly 2a, and the turbocharger rolling bearing device 1 is assembled to the inner peripheral surface of the bearing housing assembly 2a. The turbocharger rolling bearing device 1 rotatably supports an axial intermediate portion of the rotary shaft 3 between the turbine wheel 4 and the compressor impeller 5.

図２は、図１のターボチャージャー用転がり軸受装置１を拡大して示す断面図である。ターボチャージャー用転がり軸受装置１は、互いに軸方向に離れて配置されて回転軸３を回転可能に支持する一対の第１の転がり軸受２０及び第２の転がり軸受３０と、各転がり軸受２０，３０を保持する軸受ハウジング１０と、一対の転がり軸受２０，３０の間に配置されるスペーサ部材４０とを備えている。   FIG. 2 is an enlarged cross-sectional view of the turbocharger rolling bearing device 1 of FIG. The turbocharger rolling bearing device 1 includes a pair of a first rolling bearing 20 and a second rolling bearing 30 that are arranged apart from each other in the axial direction and rotatably support the rotating shaft 3, and each rolling bearing 20, 30. And a spacer member 40 disposed between the pair of rolling bearings 20 and 30.

軸受ハウジング１０は、円筒状に形成され、その一端部内周面には、タービン側の第１の転がり軸受２０が嵌込まれるハウジング部１１が形成され、他端部内周面には、コンプレッサ側の第２の転がり軸受３０が嵌込まれるハウジング部１２が形成されている。   The bearing housing 10 is formed in a cylindrical shape. A housing portion 11 into which the first rolling bearing 20 on the turbine side is fitted is formed on the inner peripheral surface of one end portion, and the compressor side is formed on the inner peripheral surface of the other end portion. A housing part 12 into which the second rolling bearing 30 is fitted is formed.

第１の転がり軸受２０は、内輪２１と、外輪２２と、内輪２１及び外輪２２の間の環状空間である軸受内部空間７に保持器２４によって保持された状態で転動可能に配設される複数の転動体（図では玉）２３とを備える。
また、第２の転がり軸受３０は、第１の転がり軸受２０と同一形状大きさに形成された内輪３１と、外輪３２と、内輪３１及び外輪３２の間の環状空間である軸受内部空間８に保持器３４によって保持された状態で転動可能に配設される複数の転動体３３とを備える。
そして、第１、第２の両転がり軸受２０，３０は、各内輪２１，３１の間にスペーサ部材４０が配設された状態で、各外輪２２，３２が軸受ハウジング１０のハウジング部１１，１２に嵌挿されて固定される。 The first rolling bearing 20 is disposed so as to be able to roll while being held by a cage 24 in an inner ring 21, an outer ring 22, and a bearing inner space 7 that is an annular space between the inner ring 21 and the outer ring 22. A plurality of rolling elements (balls in the figure) 23 are provided.
Further, the second rolling bearing 30 is formed in the bearing inner space 8 which is an inner ring 31 formed in the same shape and size as the first rolling bearing 20, an outer ring 32, and an annular space between the inner ring 31 and the outer ring 32. And a plurality of rolling elements 33 arranged so as to be able to roll while being held by the holder.
The first and second rolling bearings 20 and 30 are configured such that the outer rings 22 and 32 are the housing portions 11 and 12 of the bearing housing 10 in a state where the spacer member 40 is disposed between the inner rings 21 and 31. It is inserted and fixed to.

軸受ハウジング１０の一端部には、軸方向断面が略Ｌ字形からなる円板状のシール部材６が固定されて、軸受内部空間７の軸方向外側の開口部７ａを塞いでいる。シール部材６は、軸受ハウジング１０の一端部内周面に嵌合されて外輪２２の軸方向外側端面に当接する円筒状の固定部６ａと、固定部６ａの軸方向内側端部から軸線５０に向かって延在する円板部６ｂとを有する。シール部材６の材料としては、例えば、防錆処理された冷延鋼板のＳＰＣＣが用いられる。   A disc-shaped seal member 6 having an approximately L-shaped cross section in the axial direction is fixed to one end of the bearing housing 10 to close the axially outer opening 7 a of the bearing internal space 7. The seal member 6 is fitted to the inner peripheral surface of one end portion of the bearing housing 10 and is in contact with the outer end surface of the outer ring 22 in the axial direction. The seal member 6 faces the axial line 50 from the axially inner end portion of the fixed portion 6a. And a disc portion 6b extending. As a material of the seal member 6, for example, SPCC of a cold-rolled steel sheet that has been rust-proofed is used.

図１に示すように、本体ケース２には、送油ポンプ（図示省略）によって送油される潤滑油を導く給油路１７と、潤滑油を排出する排油路１９とが形成されている。給油路１７は、上流端が本体ケース２の外周面に開口していると共に、下流端が二股に分岐してそれぞれの油路１７ａが本体ケース２の内周面に開口している。排油路１９は、軸受ハウジング組付部２ａの軸方向中央部を貫通して形成されている。   As shown in FIG. 1, the main body case 2 is formed with an oil supply passage 17 that guides lubricating oil fed by an oil feed pump (not shown) and an oil discharge passage 19 that discharges the lubricating oil. The oil supply passage 17 has an upstream end opened to the outer peripheral surface of the main body case 2, and a downstream end branched into two branches, and each oil passage 17 a is opened to the inner peripheral surface of the main body case 2. The oil drain passage 19 is formed so as to penetrate the central portion in the axial direction of the bearing housing assembly portion 2a.

図１及び図２に示すように、本体ケース２の内周面と軸受ハウジング１０の外周面との間には、環状の隙間１８が形成されており、給油路１７に供給された潤滑油は、隙間１８に送り込まれるようになっている。なお、隙間１８は、本体ケース２と軸受ハウジング１０とをすきま嵌めすることにより形成される。これにより、隙間１８を潤滑油で満たすことで、本体ケース２の内周面と軸受ハウジング１０の外周面との間に全周に亘って油膜（オイルフィルム）が形成され、軸受ハウジング１０の振動を本体ケース２に伝わり難くしている。このように、隙間１８に満たされた潤滑油によって、回転軸３の回転に基づく振動を減衰させるオイルフィルムダンパが形成されている。   As shown in FIGS. 1 and 2, an annular gap 18 is formed between the inner peripheral surface of the main body case 2 and the outer peripheral surface of the bearing housing 10, and the lubricating oil supplied to the oil supply passage 17 is , It is fed into the gap 18. The gap 18 is formed by a loose fit between the main body case 2 and the bearing housing 10. Thus, by filling the gap 18 with lubricating oil, an oil film (oil film) is formed over the entire circumference between the inner peripheral surface of the main body case 2 and the outer peripheral surface of the bearing housing 10, and the vibration of the bearing housing 10. Is difficult to be transmitted to the main body case 2. In this way, an oil film damper that attenuates vibration based on the rotation of the rotating shaft 3 is formed by the lubricating oil filled in the gap 18.

軸受ハウジング１０の外周面の軸方向両側には、油路１７ａの開口部に対応させて、環状溝１５が周方向の全周に亘って形成されている。また、軸受ハウジング１０の外周面の軸方向中央部には、本体ケース２の排油路１９の開口部に対応させて、潤滑油を排出する排油路１９ａが形成されている。   On both axial sides of the outer peripheral surface of the bearing housing 10, annular grooves 15 are formed over the entire circumference in the circumferential direction so as to correspond to the openings of the oil passages 17a. Further, an oil drain passage 19 a for discharging the lubricating oil is formed in the axial center portion of the outer peripheral surface of the bearing housing 10 so as to correspond to the opening of the oil drain passage 19 of the main body case 2.

軸受ハウジング１０の一端部端面の径方向には、第１の転がり軸受２０に対し潤滑油を供給する油路２５が形成されている。また、軸受ハウジング１０の他端部端面の径方向には、第２の転がり軸受３０に対し潤滑油を供給する油路２６が形成されている。   An oil passage 25 that supplies lubricating oil to the first rolling bearing 20 is formed in the radial direction of the end surface of the one end portion of the bearing housing 10. An oil passage 26 that supplies lubricating oil to the second rolling bearing 30 is formed in the radial direction of the end surface of the other end portion of the bearing housing 10.

図３は、図２の要部拡大図である。図４は、図３のシール部材６を矢印Ｙの方向から見た矢視図である。図３及び図４に示すように、シール部材６の円板部６ｂは、その内径Ａが内輪２３の外径Ｂより小さく設定され、内輪２３の軸方向外側端面に径方向に重なって形成される。これにより、シール部材６は、軸受内部空間７の開口部７ａを塞いでいる。   FIG. 3 is an enlarged view of a main part of FIG. FIG. 4 is an arrow view of the seal member 6 of FIG. As shown in FIGS. 3 and 4, the disc portion 6 b of the seal member 6 is formed so that its inner diameter A is set smaller than the outer diameter B of the inner ring 23 and overlaps the axially outer end face of the inner ring 23 in the radial direction. The As a result, the seal member 6 closes the opening 7 a of the bearing internal space 7.

円板部６ｂには、軸受ハウジング１０の周囲であるハウジング外部空間９から軸受内部空間７に潤滑油を取り込むための流入部である溝６ｄと、軸受内部空間７からハウジング外部空間９に潤滑油を排出する排出孔６ｃとを備える。   The disc portion 6b includes a groove 6d that is an inflow portion for taking the lubricating oil from the housing outer space 9 around the bearing housing 10 into the bearing inner space 7, and the lubricating oil from the bearing inner space 7 to the housing outer space 9. And a discharge hole 6c.

溝６ｄは、径方向には開口部７ａの内径側端部に軸方向に対向する位置であって、周方向には同一形状からなる８個が等分配置され、径方向断面において円板部６ｂの内径側が開口して半円形状の溝に形成され、ハウジング外部空間９と軸受内部空間７とを連通して構成される。溝６ｄは、その外接円径Ｃが、内輪の外径Ｂより大きく設定されて形成される。   The grooves 6d are radially opposed to the inner diameter side end of the opening 7a in the radial direction, and are equally divided into eight pieces having the same shape in the circumferential direction. The inner diameter side of 6b is opened and formed in a semicircular groove, and the housing outer space 9 and the bearing inner space 7 are communicated with each other. The groove 6d is formed such that its circumscribed circle diameter C is set larger than the outer diameter B of the inner ring.

排出孔６ｃは、径方向には開口部７ａの外径側端部に軸方向に対向する位置であって、周方向には同一形状からなる８個が等分配置され、径方向断面において円形状に形成され、ハウジング外部空間９と軸受内部空間７とを連通して構成される。排出孔６ｃは、その外接円径Ｅが、外輪の内径Ｄ以上に設定されて形成される。   The eight discharge holes 6c are axially opposed to the outer diameter side end of the opening 7a in the radial direction, and are equally divided into eight in the circumferential direction. The housing outer space 9 and the bearing inner space 7 communicate with each other. The discharge hole 6c is formed such that its circumscribed circle diameter E is set to be equal to or larger than the inner diameter D of the outer ring.

溝６ｄ及び排出孔６ｃは、互いに周方向に異なる位置に設けられている。これにより、ターボチャージャー用転がり軸受装置１では、軸受内部空間７に流入した潤滑油が直ぐに排出することなく、潤滑した後に排出されるので、軸受内部が適正に潤滑される。   The groove 6d and the discharge hole 6c are provided at different positions in the circumferential direction. As a result, in the turbocharger rolling bearing device 1, the lubricating oil that has flowed into the bearing internal space 7 is discharged immediately after being lubricated without being immediately discharged, so that the inside of the bearing is properly lubricated.

本実施形態に係るターボチャージャー用転がり軸受装置１によれば、ターボチャージャーＴの作動時において、本体ケース１の給油路１７に供給される潤滑油は、油路１７ａ、隙間１８、及び油路２５を経た後、シール部材６の溝６ｄから軸受内部空間７に流入する。流入した潤滑油により、第１の転がり軸受２０が潤滑及び冷却される。この潤滑油は、排油路１９ａ及び排油路１９を経て排出される。そして、排出された潤滑油は、送油ポンプにより送油されて循環する。   According to the turbocharger rolling bearing device 1 according to the present embodiment, when the turbocharger T is operated, the lubricating oil supplied to the oil supply passage 17 of the main body case 1 is the oil passage 17a, the gap 18, and the oil passage 25. After passing through, it flows into the bearing internal space 7 from the groove 6d of the seal member 6. The first rolling bearing 20 is lubricated and cooled by the flowing lubricating oil. The lubricating oil is discharged through the oil discharge passage 19 a and the oil discharge passage 19. Then, the discharged lubricating oil is fed by an oil feeding pump and circulated.

これにより、ターボチャージャー用転がり軸受装置１では、油路２５からの潤滑油は、シール部材６により開口部７ａから軸受内部空間７への流入が制限されるので、第１の転がり軸受２０における潤滑油の攪拌抵抗によるトルク損失を軽減することができる。   Thereby, in the turbocharger rolling bearing device 1, the lubricating oil from the oil passage 25 is restricted from flowing into the bearing internal space 7 from the opening 7 a by the seal member 6, so that lubrication in the first rolling bearing 20 is performed. Torque loss due to oil agitation resistance can be reduced.

また、ターボチャージャー用転がり軸受装置１では、開口部７ａの最内径端に形成される溝６ｄから軸受内部空間７に潤滑油が流入するので、潤滑油が不足しやすい内輪２１側が適正に潤滑される。   Further, in the turbocharger rolling bearing device 1, since the lubricating oil flows into the bearing inner space 7 from the groove 6d formed at the innermost end of the opening 7a, the inner ring 21 side where the lubricating oil tends to be insufficient is appropriately lubricated. The

また、このターボチャージャー用転がり軸受装置１では、溝６ｄの配置や大きさ等により軸受内部空間７への潤滑油の流入量を調整できる。   Further, in this turbocharger rolling bearing device 1, the amount of lubricating oil flowing into the bearing internal space 7 can be adjusted by the arrangement and size of the grooves 6d.

また、ターボチャージャー用転がり軸受装置１では、回転軸３が回転することにより、軸受内部空間７の潤滑油が径方向外方へ移動して、開口部７ａの最外径端に対向して形成されるシール部材６の排出孔６ｃから図３に示す矢印Ｆの方向に排出されるので、スムースに排出できて転がり軸受における潤滑油の攪拌抵抗によるトルク損失を軽減することができる。   Further, in the turbocharger rolling bearing device 1, when the rotary shaft 3 rotates, the lubricating oil in the bearing inner space 7 moves outward in the radial direction, and is formed to face the outermost diameter end of the opening 7 a. Since it is discharged from the discharge hole 6c of the seal member 6 in the direction of the arrow F shown in FIG. 3, it can be discharged smoothly and torque loss due to the agitation resistance of the lubricating oil in the rolling bearing can be reduced.

ここで、ターボチャージャー用転がり軸受装置１では、回転軸３が高速で回転して第１、第２の両転がり軸受２０，３０が高速回転する場合、軸受の冷却が必要になるので、保持器２４，３４が潤滑油を巻き込んで軸受内部空間７，８に流入させることにより、軸受を適正に潤滑している。   Here, in the turbocharger rolling bearing device 1, when the rotary shaft 3 rotates at a high speed and the first and second rolling bearings 20 and 30 rotate at a high speed, the bearing needs to be cooled. The bearings 24 and 34 entrain the lubricating oil and flow into the bearing internal spaces 7 and 8 to properly lubricate the bearings.

また、ターボチャージャー用転がり軸受装置１では、ターボチャージャーＴの作動時において、本体ケース１の給油路１７に供給される潤滑油は、油路１７ａ、隙間１８、及び油路２６を経た後、第１の転がり軸受２０に同様、第２の転がり軸受３０の開口部から軸受内部空間８に流入する。流入した潤滑油により、第２の転がり軸受３０が潤滑及び冷却される。この潤滑油は、排油路１９ａ及び排油路１９を経て排出される。そして、排出された潤滑油は、送油ポンプにより送油されて循環する。   In the turbocharger rolling bearing device 1, when the turbocharger T is operated, the lubricating oil supplied to the oil supply passage 17 of the main body case 1 passes through the oil passage 17 a, the gap 18, and the oil passage 26, and then Similarly to the first rolling bearing 20, it flows into the bearing internal space 8 from the opening of the second rolling bearing 30. The second rolling bearing 30 is lubricated and cooled by the flowing lubricating oil. The lubricating oil is discharged through the oil discharge passage 19 a and the oil discharge passage 19. Then, the discharged lubricating oil is fed by an oil feeding pump and circulated.

なお、本発明は本実施形態に限定するものではなく、本発明の要旨を逸脱しない範囲内において、種々の形態で実施することができる。
本実施形態では、溝６ｄは、径方向断面において円板部６ｂの内径側が開口して半円形状の溝に形成されるとしたが、それに限るものではなく、例えば、円板部６ｂの内径側が開口していない孔形状の流入孔であっても良く、また、これらの溝及び孔の形状は、円や四角等であっても良い。 In addition, this invention is not limited to this embodiment, In the range which does not deviate from the summary of this invention, it can implement with a various form.
In the present embodiment, the groove 6d is formed in a semicircular groove with the inner diameter side of the disk portion 6b opened in the radial cross section. However, the present invention is not limited to this, for example, the inner diameter of the disk portion 6b. The shape of the grooves and the holes may be a circle, a square, or the like.

また、本実施形態では、溝６ｄ及び排出孔６ｃが周方向の８箇所に等配されるとしたが、それに限るものではなく、例えば、それぞれが２箇所、４箇所でも良く、ターボチャージャー用転がり軸受装置１の環境条件等により適宜決定すれば良い。   Further, in the present embodiment, the grooves 6d and the discharge holes 6c are equally distributed at eight places in the circumferential direction, but the present invention is not limited to this, and for example, there may be two places and four places. What is necessary is just to determine suitably with the environmental conditions etc. of the bearing apparatus 1.

＜第２実施形態＞
第１実施形態におけるターボチャージャー用転がり軸受装置１では、軸受内部空間７に潤滑油を取り込むシール部材６の流入部が溝６ｄにより形成されるが、第２実施形態では、流入部６ｄ１が帯状に全周に亘って形成される構成の実施形態である。第２実施形態において、第１実施形態と同一の構成の説明は、簡略化のため省略する。 Second Embodiment
In the turbocharger rolling bearing device 1 according to the first embodiment, the inflow portion of the seal member 6 that takes the lubricating oil into the bearing internal space 7 is formed by the groove 6d. It is embodiment of the structure formed over a perimeter. In the second embodiment, the description of the same configuration as that of the first embodiment is omitted for the sake of brevity.

図５は、本発明の一実施形態に係るターボチャージャー用転がり軸受装置１を備えたターボチャージャーＴの要部拡大断面図である。図６は、図５のシール部材６を矢印Ｙ１の方向から見た矢視図である。図５及び図６に示すように、シール部材６の円板部６ｂは、その内径Ｃ１が内輪２３の外径Ｂより大きく設定されて形成される。これにより、シール部材６は、軸受内部空間７の開口部７ａを塞いでいる。   FIG. 5 is an enlarged cross-sectional view of a main part of a turbocharger T including the turbocharger rolling bearing device 1 according to an embodiment of the present invention. FIG. 6 is an arrow view of the seal member 6 of FIG. 5 as viewed from the direction of the arrow Y1. As shown in FIGS. 5 and 6, the disc portion 6 b of the seal member 6 is formed such that the inner diameter C <b> 1 is set larger than the outer diameter B of the inner ring 23. As a result, the seal member 6 closes the opening 7 a of the bearing internal space 7.

ターボチャージャー用転がり軸受装置１には、円板部６ｂの内径Ｃ１と内輪２３の外径Ｂとの間に帯状に全周に亘って流入部６ｄ１が形成される。このように、ターボチャージャー用転がり軸受装置１では、流入部６ｄ１が、シール部材６と内輪２３との間に環状の隙間を形成してハウジング外部空間９と軸受内部空間７とを連通し、ハウジング外部空間９の潤滑油を軸受内部空間７に取り込む。   In the turbocharger rolling bearing device 1, an inflow portion 6 d 1 is formed in a belt shape between the inner diameter C <b> 1 of the disc portion 6 b and the outer diameter B of the inner ring 23 over the entire circumference. Thus, in the turbocharger rolling bearing device 1, the inflow portion 6 d 1 forms an annular gap between the seal member 6 and the inner ring 23 to communicate the housing outer space 9 and the bearing inner space 7. The lubricating oil in the external space 9 is taken into the bearing internal space 7.

本実施形態に係るターボチャージャー用転がり軸受装置１によれば、第１実施形態の作用効果に加え、流入部６ｄ１が開口部７ａの全周に亘って形成されるので、周方向にバランス良く潤滑される。   According to the rolling bearing device for turbocharger 1 according to the present embodiment, in addition to the operational effects of the first embodiment, the inflow portion 6d1 is formed over the entire circumference of the opening portion 7a, so that lubrication is performed with a good balance in the circumferential direction. Is done.

なお、第１、第２実施形態では、シール部材６が軸受ハウジング１０の一端部内周面に嵌合されるとしたが、それに限るものではなく、例えば、軸受ハウジング１０の一端部内周面又は／及び外輪２２の軸方向外側端面に接着して固定する構成に適用しても良い。   In the first and second embodiments, the seal member 6 is fitted to the inner peripheral surface of the one end portion of the bearing housing 10. However, the present invention is not limited to this. For example, the inner peripheral surface of the one end portion of the bearing housing 10 or / Further, the present invention may be applied to a configuration in which the outer ring 22 is bonded and fixed to the outer end surface in the axial direction.

また、第１、第２実施形態では、シール部材６が軸受ハウジング１０の一端部に固定されるとしたが、それに限るものではなく、例えば、軸受ハウジング１０の他端部にも固定される構成、又は、軸受ハウジング１０の他端部のみに固定される構成に適用しても良い。   In the first and second embodiments, the seal member 6 is fixed to one end portion of the bearing housing 10. However, the present invention is not limited to this. For example, the seal member 6 is also fixed to the other end portion of the bearing housing 10. Or you may apply to the structure fixed only to the other end part of the bearing housing 10. FIG.

１：ターボチャージャー用転がり軸受装置、 ２：本体ケース、 ２ａ：軸受ハウジング組付部、 ３：回転軸、 ４：タービンホイール、 ４ａ：排気流路、 ５：コンプレッサインペラ、 ５ａ：吸気流路、 ６：シール部材、 ６ａ：固定部、 ６ｂ：円板部、 ６ｃ：溝（流入部）、 ６ｄ：排出孔、 ６ｄ１：流入部、 ７，８：軸受内部空間、 ７ａ：開口部、 ９：ハウジング外部空間、 １０：軸受ハウジング、 １１，１２：ハウジング部、 １５：環状溝、 １７：給油路、 １７ａ：油路、 １８：隙間、 １９，１９ａ：排油路、 ２０：第１の転がり軸受、 ２１：内輪、 ２２：外輪、 ２３：転動体、 ２４：保持器、 ２５，２６：油路、 ３０：第２の転がり軸受、 ３１：内輪、 ３２：外輪、 ３３：転動体、 ３４：保持器、 ４０：スペーサ部材、 ５０：軸線、 Ａ：シール部材の内径、 Ｂ：内輪の外径、 Ｃ：溝の外接円径、 Ｃ１：シール部材の内径、 Ｄ：外輪の内径、 Ｅ：排出孔の外接円径、 Ｔ：ターボチャージャー 1: rolling bearing device for turbocharger, 2: body case, 2a: bearing housing assembly, 3: rotating shaft, 4: turbine wheel, 4a: exhaust passage, 5: compressor impeller, 5a: intake passage, 6 : Seal member, 6a: fixed part, 6b: disk part, 6c: groove (inflow part), 6d: discharge hole, 6d1: inflow part, 7, 8: bearing internal space, 7a: opening, 9: outside of housing Space, 10: bearing housing, 11, 12: housing portion, 15: annular groove, 17: oil supply passage, 17a: oil passage, 18: gap, 19, 19a: oil discharge passage, 20: first rolling bearing, 21 : Inner ring, 22: outer ring, 23: rolling element, 24: cage, 25, 26: oil passage, 30: second rolling bearing, 31: inner ring, 32: outer ring, 33: rolling element, 34: holding 40: spacer member, 50: axis, A: inner diameter of seal member, B: outer diameter of inner ring, C: circumscribed circle diameter of groove, C1: inner diameter of seal member, D: inner diameter of outer ring, E: discharge hole Circumscribed circle diameter, T: turbocharger

Claims (5)

互いに軸方向に離れて配置され、ターボチャージャーの回転軸を回転自在に支持する一対の転がり軸受と、
前記一対の軸受の外輪のそれぞれが軸方向の両端部内周面に嵌合される円筒状の軸受ハウジングと、を備え、
前記軸受ハウジングは、前記ターボチャージャーの本体ケース内に装着され、
前記軸受ハウジングの周囲と前記本体ケースの内周面との間の環状の隙間に潤滑油を満たしてオイルフィルムが形成され、
前記転がり軸受には、その内外輪間に環状の軸受内部空間が形成され、
前記潤滑油は、前記軸受ハウジングの周囲から前記軸受内部空間に流入して循環するターボチャージャー用転がり軸受装置であって、
前記軸受ハウジングの軸方向の両端部又はいずれか一方の端部に配置され、前記軸受内部空間の開口部を塞ぐ円板状のシール部材をさらに備え、
前記シール部材は、前記外輪の軸方向外側端面と前記軸受ハウジングの端部内周面との両方又はいずれか一方に固定される固定部と、この固定部から軸受の軸線に向かって延在し前記内輪の軸方向外側端面に径方向に重なって形成される円板部とを有し、
前記円板部は、前記開口部の内径側端部に軸方向に対向する位置に形成され前記軸受ハウジングの周囲であるハウジング外部空間と前記軸受内部空間とを連通する流入部と、
前記開口部の外径側端部に軸方向に対向する位置に形成され前記ハウジング外部空間と前記軸受内部空間とを連通する排出孔とを備えることを特徴とするターボチャージャー用転がり軸受装置。 A pair of rolling bearings arranged axially apart from each other and rotatably supporting the rotating shaft of the turbocharger;
Each of the outer rings of the pair of bearings includes a cylindrical bearing housing fitted to the inner peripheral surfaces of both end portions in the axial direction,
The bearing housing is mounted in a body case of the turbocharger;
An oil film is formed by filling lubricating oil in an annular gap between the periphery of the bearing housing and the inner peripheral surface of the main body case,
In the rolling bearing, an annular bearing internal space is formed between the inner and outer rings,
The lubricating oil is a rolling bearing device for a turbocharger that flows into the bearing internal space from the periphery of the bearing housing and circulates,
A disc-shaped seal member that is disposed at either or both ends of the bearing housing in the axial direction and closes the opening of the bearing internal space;
The seal member is fixed to both or either one of the axially outer end surface of the outer ring and the inner peripheral surface of the end portion of the bearing housing, and extends from the fixed portion toward the bearing axis. A disk part formed to overlap the axially outer end face of the inner ring in the radial direction,
The disc portion is formed at a position facing the inner diameter side end of the opening in the axial direction, and an inflow portion communicating the housing outer space and the bearing inner space around the bearing housing;
A rolling bearing device for a turbocharger, comprising: a discharge hole formed at a position facing an outer diameter side end of the opening in the axial direction and communicating the housing outer space and the bearing inner space. 前記排出孔は、その外接円径が前記外輪の内径以上に設定されて形成されることを特徴とする請求項１に記載のターボチャージャー用転がり軸受装置。   2. The rolling bearing device for a turbocharger according to claim 1, wherein the discharge hole is formed with a circumscribed circle diameter set to be equal to or larger than an inner diameter of the outer ring. 前記流入部は前記円板部の内径側が開口した溝又は孔形状の流入孔からなり、この溝又は流入孔の外接円径は、前記内輪の外径より大きく設定されることを特徴とする請求項１又は請求項２に記載のターボチャージャー用転がり軸受装置。   The inflow portion includes a groove or a hole-shaped inflow hole opened on an inner diameter side of the disk portion, and a circumscribed circle diameter of the groove or the inflow hole is set larger than an outer diameter of the inner ring. The rolling bearing device for turbochargers according to claim 1 or 2. 前記流入部は前記円板部の内径端から帯状に全周に亘って形成され、前記流入部を除いた前記円板部の内径は、前記内輪の外径より大きく設定されることを特徴とする請求項１又は請求項２に記載のターボチャージャー用転がり軸受装置。   The inflow portion is formed from the inner diameter end of the disc portion over the entire circumference in a band shape, and the inner diameter of the disc portion excluding the inflow portion is set larger than the outer diameter of the inner ring. A rolling bearing device for a turbocharger according to claim 1 or 2. 前記流入部及び前記排出孔は、互いに周方向に異なる位置に設けられることを特徴とする請求項３に記載のターボチャージャー用転がり軸受装置。   The rolling bearing device for a turbocharger according to claim 3, wherein the inflow portion and the discharge hole are provided at different positions in the circumferential direction.
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