JP5974597B2 - Rolling bearing device for turbocharger - Google Patents

Rolling bearing device for turbocharger Download PDF

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Publication number
JP5974597B2
JP5974597B2 JP2012088148A JP2012088148A JP5974597B2 JP 5974597 B2 JP5974597 B2 JP 5974597B2 JP 2012088148 A JP2012088148 A JP 2012088148A JP 2012088148 A JP2012088148 A JP 2012088148A JP 5974597 B2 JP5974597 B2 JP 5974597B2
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rolling bearing
supply hole
oil supply
turbocharger
housing
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JP2013217436A (en
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山口　晋弘
晋弘 山口
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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
    • 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
    • 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

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Supercharger (AREA)
  • Rolling Contact Bearings (AREA)

Description

この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.

従来、ターボチャージャー用転がり軸受装置としては、例えば、特許文献１に開示されている。
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４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。 Conventionally, a rolling bearing device for a turbocharger is disclosed in, for example, Patent Document 1.
In such a turbocharger rolling bearing device, as shown in FIG. 4, 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 is excessive when 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、タービン側の第１の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 first rolling bearing on the turbine side.

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、軸受ハウジングに対し、一端部にタービンホイールが配設され他端部にコンプレッサインペラが配設されるターボチャージャーの回転軸を、タービン側の第１の転がり軸受とコンプレッサ側の第２の転がり軸受を介して回転可能に支持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タービン側端部には、前記タービンホイール側に向けて突出する延長ハウジング部が形成され、前記延長ハウジング部には、前記回転軸の外周面に向けて潤滑油を供給する給油孔が形成される一方、前記回転軸の前記給油孔に対向する軸部分の外周面には、前記給油孔から噴出される潤滑油を前記第１の転がり軸受側と前記タービンホイール側とに分配する分配鍔部が形成されてされており、
前記分配鍔部は、軸方向の両端から中央部に向けてしだいに大径に形成されて軸方向断面が山形状に形成され、前記分配鍔部の最大径をなす頂部が前記給油孔に臨んでい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 turbo with a turbine wheel disposed at one end and a compressor impeller disposed at the other end relative to the bearing housing. A turbocharger rolling bearing device that rotatably supports a rotating shaft of a charger via a first rolling bearing on a turbine side and a second rolling bearing on a compressor side, and is provided at a turbine side end of the bearing housing. Is formed with an extension housing portion projecting toward the turbine wheel side, and the extension housing portion has an oil supply hole for supplying lubricating oil toward the outer peripheral surface of the rotation shaft, while the rotation shaft On the outer peripheral surface of the shaft portion facing the oil supply hole, lubricant oil ejected from the oil supply hole is placed on the first rolling bearing side and the turbine ho Over distribution flange portion to be distributed to the Le side are formed,
The distribution saddle portion is gradually formed with a large diameter from both ends in the axial direction toward the central portion, and the axial cross section is formed in a mountain shape, and the top portion that forms the maximum diameter of the distribution flange portion faces the oil supply hole. and characterized in that out.

前記構成によると、軸受ハウジングの延長ハウジング部に形成された給油孔から噴出される潤滑油は、回転軸の分配鍔部において第１の転がり軸受側とタービンホイール側とに分配されるため、従来の軸受ハウジングのジェット給油孔から第１の転がり軸受に向けて潤滑油が直接的に噴出される場合と比べ、第１の転がり軸受に対する潤滑油の供給量が過大となることが抑制される。
この結果、第１の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 above configuration, the lubricating oil ejected from the oil supply hole formed in the extension housing portion of the bearing housing is distributed to the first rolling bearing side and the turbine wheel side in the distribution collar portion of the rotating shaft. Compared to the case where the lubricating oil is directly ejected from the jet oil supply hole of the bearing housing toward the first rolling bearing, the supply amount of the lubricating oil to the first rolling bearing is suppressed from being excessive.
As a result, torque loss due to the agitation resistance of the lubricating oil in the first rolling bearing can be reduced.

また、前記構成によると、軸方向断面が山形状に形成された分配鍔部の頂部が給油孔に臨むことで、給油孔から噴出される潤滑油を、第１の転がり軸受側とタービンホイール側とに二分して分配することができる。

 In addition, according to the above configuration, the top portion of the distribution rod portion whose axial cross section is formed in a mountain shape faces the oil supply hole, so that the lubricant sprayed from the oil supply hole can be supplied to the first rolling bearing side and the turbine wheel side. It can be divided in half.

この発明の実施例１に係るターボチャージャー用転がり軸受装置を示す縦断面図である。It is a longitudinal cross-sectional view which shows the rolling bearing apparatus for turbochargers which concerns on Example 1 of this invention. ターボチャージャー用転がり軸受装置を拡大して示す縦断面図である。It is a longitudinal cross-sectional view which expands and shows the rolling bearing apparatus for turbochargers. 給油孔から噴出される潤滑油が、分配鍔部によって第１の転がり軸受側とタービンホイール側とに二分して分配される状態を示す説明図である。It is explanatory drawing which shows the state by which the lubricating oil injected from an oil supply hole is divided by the distribution collar part into the 1st rolling bearing side and the turbine wheel side. 従来のターボチャージャー用転がり軸受装置を示す縦断面図である。It is a longitudinal cross-sectional view which shows the conventional rolling bearing device for turbochargers.

この発明を実施するための形態について実施例にしたがって説明する。   A mode for carrying out the present invention will be described in accordance with an embodiment.

この発明の実施例１を図１〜図３にしたがって説明する。
図１と図２に示すように、ターボチャージャーの本体ケース１には、軸受ハウジング組付部２が形成され、この軸受ハウジング組付部２には、その内周面との間にオイルフィルムを構成する環状の隙間をもって軸受ハウジング１０が組み付けられる。
軸受ハウジング１０には、ターボチャージャーの回転軸３が第１の転がり軸受２０と第２の転がり軸受３０とを介して回転可能に支持される。
なお、ターボチャージャーの回転軸３の一端部にはタービンホイール４が配設され、他端部にはコンプレッサインペラ５が配設される。 A first embodiment of the present invention will be described with reference to FIGS.
As shown in FIGS. 1 and 2, a turbocharger body case 1 is formed with a bearing housing assembly 2, and an oil film is provided between the bearing housing assembly 2 and the inner peripheral surface thereof. The bearing housing 10 is assembled with an annular gap.
A rotating shaft 3 of a turbocharger is rotatably supported on the bearing housing 10 via a first rolling bearing 20 and a second rolling bearing 30.
A turbine wheel 4 is disposed at one end of the rotating shaft 3 of the turbocharger, and a compressor impeller 5 is disposed at the other end.

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.

図２に示すように、第１の転がり軸受２０は、内輪２１と、外輪２２と、これら内・外輪２１、２２の間の環状空間に保持器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、複数の転動体３３と保持器３４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。 As shown in FIG. 2, the first rolling bearing 20 is arranged so as to be able to roll while being held by an inner ring 21, an outer ring 22, and an annular space between the inner and outer rings 21, 22 by a cage 24. A plurality of rolling elements (balls in the figure) 23 are provided.
Further, the second rolling bearing 30 includes an inner ring 31 formed in the same shape and size as the first rolling bearing 20, an outer ring 32, a plurality of rolling elements 33, and a cage 34.
In the first and second rolling bearings 20 and 30, the spacer members 40 are disposed between the inner rings 21 and 31, and the outer rings 22 and 32 are the housing portions 11 and 12 of the bearing housing 10. It is inserted and fixed to.

図１と図２に示すように、軸受ハウジング１０の外周面の両端部寄り部分には、縦断面Ｖ溝状の環状溝（油溝）１５、１６がそれぞれ形成されている。なお、本体ケース１には油路１ａが形成されている。   As shown in FIG. 1 and FIG. 2, annular grooves (oil grooves) 15 and 16 having a V-shaped longitudinal section are formed in portions near both ends of the outer peripheral surface of the bearing housing 10. An oil passage 1 a is formed in the main body case 1.

図２と図３に示すように、軸受ハウジング１０のタービン側のハウジング部１１の端部には、タービンホイール４側に向けて突出する延長ハウジング部１３が形成されている。
延長ハウジング部１３には、回転軸３の外周面に向けて潤滑油を供給する給油孔１７が形成されている。この給油孔１７は、軸受ハウジング１０のタービン側の環状溝１５に連通溝１８を介して連通されている。
また、連通溝１８は、軸受ハウジング１０のタービン側の環状溝１５の部分から延長ハウジング部１３の外周面の軸方向にわたって形成されている。 As shown in FIGS. 2 and 3, an extension housing portion 13 that protrudes toward the turbine wheel 4 side is formed at an end portion of the turbine housing portion 11 of the bearing housing 10.
The extension housing part 13 is formed with an oil supply hole 17 for supplying lubricating oil toward the outer peripheral surface of the rotary shaft 3. The oil supply hole 17 communicates with the annular groove 15 on the turbine side of the bearing housing 10 via a communication groove 18.
Further, the communication groove 18 is formed from the portion of the annular groove 15 on the turbine side of the bearing housing 10 to the axial direction of the outer peripheral surface of the extension housing portion 13.

一方、給油孔１７に対向する回転軸３の軸部分の外周面には、給油孔１７から噴出される潤滑油を第１の転がり軸受２０側とタービンホイール４側とに分配する分配鍔部６が形成されている。
この実施例１において、分配鍔部６は、軸方向の両端から中央部に向けてしだいに大径に形成されて軸方向断面が山形状に形成されている。
そして、分配鍔部６は、最大径をなす頂部６ａと、両傾斜面７、８とを有し、頂部６ａが給油孔１７の中心部に臨んでいる。 On the other hand, on the outer peripheral surface of the shaft portion of the rotary shaft 3 that faces the oil supply hole 17, the distribution flange 6 that distributes the lubricating oil ejected from the oil supply hole 17 to the first rolling bearing 20 side and the turbine wheel 4 side. Is formed.
In the first embodiment, the distribution collar portion 6 is gradually formed to have a large diameter from both ends in the axial direction toward the central portion, and the axial cross section is formed in a mountain shape.
The distribution rod portion 6 has a top portion 6 a having a maximum diameter and both inclined surfaces 7 and 8, and the top portion 6 a faces the center portion of the oil supply hole 17.

また、この実施例１において、図２に示すように、軸受ハウジング１０のコンプレッサインペラ５側の端面の径方向には、第２の転がり軸受３０に対し潤滑油を供給する油溝２５が形成されている。
また、軸受ハウジング１０の下部の両ハウジング部１１、１２の間に位置する部分（この実施例１では軸方向中央部）には、潤滑油の排出孔１９が形成されている。 Further, in the first embodiment, as shown in FIG. 2, an oil groove 25 for supplying lubricating oil to the second rolling bearing 30 is formed in the radial direction of the end surface on the compressor impeller 5 side of the bearing housing 10. ing.
A lubricating oil discharge hole 19 is formed in a portion located between the housing portions 11 and 12 at the lower portion of the bearing housing 10 (in the axial direction central portion in the first embodiment).

この実施例１に係るターボチャージャー用転がり軸受装置は上述したように構成される。
したがって、ターボチャージャーの作動時において、本体ケース１の油路１ａに供給される潤滑油は、軸受ハウジング１０のタービン側の環状溝１５及び連通溝１８を経た後、軸受ハウジング１０の延長ハウジング部１３の給油孔１７から回転軸３の分配鍔部６に向けて噴出される。
そして、給油孔１７から噴出される潤滑油が回転軸３の分配鍔部６の両傾斜面７、８に衝突して跳ね返ることで、第１の転がり軸受２０側とタービンホイール４側とに分配される。
このため、従来の軸受ハウジングのジェット給油孔から第１の転がり軸受に向けて潤滑油が直接的に噴出される場合と比べ、第１の転がり軸受２０に対する潤滑油の供給量が過大となることが抑制される。
この結果、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。 The turbocharger rolling bearing device according to the first embodiment is configured as described above.
Therefore, during the operation of the turbocharger, the lubricating oil supplied to the oil passage 1 a of the main body case 1 passes through the annular groove 15 and the communication groove 18 on the turbine side of the bearing housing 10 and then the extended housing portion 13 of the bearing housing 10. From the oil supply hole 17 toward the distribution rod portion 6 of the rotary shaft 3.
Then, the lubricating oil ejected from the oil supply hole 17 collides with both inclined surfaces 7 and 8 of the distribution rod portion 6 of the rotating shaft 3 and bounces back, thereby distributing the oil to the first rolling bearing 20 side and the turbine wheel 4 side. Is done.
For this reason, compared with the case where the lubricating oil is directly jetted from the jet oil supply hole of the conventional bearing housing toward the first rolling bearing, the supply amount of the lubricating oil to the first rolling bearing 20 becomes excessive. Is suppressed.
As a result, torque loss due to the stirring resistance of the lubricating oil in the first rolling bearing 20 can be reduced.

また、この実施例１において、軸方向断面が山形状に形成された分配鍔部６の頂部６ａが給油孔１７の中心部に臨むことで、給油孔１７から噴出される潤滑油を、分配鍔部６の両傾斜面７、８によって第１の転がり軸受２０側とタービンホイール４側とに二分して分配することができる。   Further, in the first embodiment, the top portion 6a of the distribution rod portion 6 whose axial cross section is formed in a mountain shape faces the central portion of the oil supply hole 17, so that the lubricating oil ejected from the oil supply hole 17 is distributed. The two inclined surfaces 7 and 8 of the portion 6 can be divided into two parts, the first rolling bearing 20 side and the turbine wheel 4 side.

なお、この発明は前記実施例１に限定するものではなく、この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。   In addition, this invention is not limited to the said Example 1, In the range which does not deviate from the summary of this invention, it can implement with a various form.

１ 本体ケース
３ 回転軸
６ 分配鍔部
６ａ 頂部
７、８ 傾斜面
１０ 軸受ハウジング
１１、１２ ハウジング部
１３ 延長ハウジング部
１５、１６ 環状溝
１７ 給油孔
２０ 第１の転がり軸受
３０ 第２の転がり軸受
４０ スペーサ部材 DESCRIPTION OF SYMBOLS 1 Main body case 3 Rotating shaft 6 Distribution collar part 6a Top part 7, 8 Inclined surface 10 Bearing housing 11, 12 Housing part 13 Extension housing part 15, 16 Annular groove 17 Oil supply hole 20 1st rolling bearing 30 2nd rolling bearing 40 Spacer member

Claims (1)

軸受ハウジングに対し、一端部にタービンホイールが配設され他端部にコンプレッサインペラが配設されるターボチャージャーの回転軸を、タービン側の第１の転がり軸受とコンプレッサ側の第２の転がり軸受を介して回転可能に支持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タービン側端部には、前記タービンホイール側に向けて突出する延長ハウジング部が形成され、
前記延長ハウジング部には、前記回転軸の外周面に向けて潤滑油を供給する給油孔が形成される一方、
前記回転軸の前記給油孔に対向する軸部分の外周面には、前記給油孔から噴出される潤滑油を前記第１の転がり軸受側と前記タービンホイール側とに分配する分配鍔部が形成されており、
前記分配鍔部は、軸方向の両端から中央部に向けてしだいに大径に形成されて軸方向断面が山形状に形成され、
前記分配鍔部の最大径をなす頂部が前記給油孔に臨んでい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。 With respect to the bearing housing, a turbocharger shaft having a turbine wheel disposed at one end and a compressor impeller disposed at the other end is connected to a first rolling bearing on the turbine side and a second rolling bearing on the compressor side. A rolling bearing device for a turbocharger that is rotatably supported via
An extension housing portion protruding toward the turbine wheel side is formed at the turbine side end portion of the bearing housing,
In the extension housing part, an oil supply hole for supplying lubricating oil toward the outer peripheral surface of the rotating shaft is formed,
On the outer peripheral surface of the shaft portion of the rotating shaft that faces the oil supply hole, a distribution rod portion that distributes the lubricating oil ejected from the oil supply hole to the first rolling bearing side and the turbine wheel side is formed. and,
The distribution saddle portion is gradually formed in a large diameter from both ends in the axial direction toward the central portion, and the axial cross section is formed in a mountain shape,
A rolling bearing device for a turbocharger, characterized in that a top portion forming the maximum diameter of the distribution flange portion faces the oil supply hole .
JP2012088148A 2012-04-09 2012-04-09 Rolling bearing device for turbocharger Expired - Fee Related JP5974597B2 (en)

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WO2017094187A1 (en) 2015-12-04 2017-06-08 三菱重工業株式会社 Turbocharger, engine system, and control method for turbocharger
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EP3379053B1 (en) 2015-12-25 2021-11-10 Mitsubishi Heavy Industries Engine & Turbocharger, Ltd. Turbocharger
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