JP2016037987A - Bearing device for turbocharger - Google Patents

Bearing device for turbocharger Download PDF

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Publication number
JP2016037987A
JP2016037987A JP2014160047A JP2014160047A JP2016037987A JP 2016037987 A JP2016037987 A JP 2016037987A JP 2014160047 A JP2014160047 A JP 2014160047A JP 2014160047 A JP2014160047 A JP 2014160047A JP 2016037987 A JP2016037987 A JP 2016037987A
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Japan
Prior art keywords
oil
bearing
rolling bearing
bearing device
turbocharger
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JP2014160047A
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JP6352101B2 (en
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中尾　吾朗
Goro Nakao
吾朗 中尾
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NTN Corp
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NTN Corp
NTN Toyo Bearing Co Ltd
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Priority to JP2014160047A priority Critical patent/JP6352101B2/en
Priority to PCT/JP2015/071766 priority patent/WO2016021489A1/en
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B39/00—Component parts, details, or accessories relating to, driven charging or scavenging pumps, not provided for in groups F02B33/00 - F02B37/00
    • 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
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B39/00—Component parts, details, or accessories relating to, driven charging or scavenging pumps, not provided for in groups F02B33/00 - F02B37/00
    • F02B39/14—Lubrication of pumps; Safety measures therefor
    • 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
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C37/00—Cooling of bearings
    • F16C37/007—Cooling of bearings of rolling bearings

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Supercharger (AREA)
  • Mounting Of Bearings Or Others (AREA)
  • Rolling Contact Bearings (AREA)

Abstract

PROBLEM TO BE SOLVED: To provide a bearing device for a turbocharger which can suppress that the rotation of a rolling bearing for rotatably supporting a turbine shaft is inhibited by lubrication oil.SOLUTION: A pair of annular protrusions 11 for positioning an outer ring 31 of a rolling bearing 30 into an axial direction are formed at an internal periphery of a bearing case 10 which is incorporated with a bearing 30 which rotatably supports a turbine shaft 20, and peripheral grooves 12 having V-shapes at cross sections are formed at internal peripheries of the respective annular protrusions 11. A radial oil supply hole 14 is formed at the bearing case 10, oil which is supplied into the peripheral grooves 12 from the oil supply hole 14 is moved along internal peripheral faces of the peripheral grooves 12, and circulated, the circulated oil is made to flow into the rolling bearing 30, and the rolling bearing 30 is lubricated and cooled.SELECTED DRAWING: Figure 1

Description

この発明は、ターボチャージャのタービン軸を回転自在に支持するターボチャージャ用軸受装置に関する。   The present invention relates to a turbocharger bearing device that rotatably supports a turbine shaft of a turbocharger.

エンジンの排気ガスによりタービンホイールを回転させ、そのタービンホイールと同軸上に設けられたコンプレッサホイールを回転させることにより吸入空気を圧縮してシリンダ内に送り込み、エンジンの出力を増大させるターボチャージャにおいては、タービン軸の回転抵抗が性能に大きく影響するため、タービン軸を転がり軸受で回転自在に支持する場合が多くなってきている。   In the turbocharger that rotates the turbine wheel by the exhaust gas of the engine, and compresses the intake air by rotating the compressor wheel provided coaxially with the turbine wheel to increase the engine output. Since the rotational resistance of the turbine shaft greatly affects the performance, the turbine shaft is often supported rotatably by a rolling bearing.

この場合、転がり軸受はタービン軸と共に高速回転して高温になり易く、潤滑が不十分であると焼き付きが生じるため、エンジンオイルでもって転がり軸受を潤滑し、冷却することが行われている。   In this case, the rolling bearing rotates with the turbine shaft at a high speed and easily reaches a high temperature, and seizure occurs when the lubrication is insufficient. Therefore, the rolling bearing is lubricated and cooled with engine oil.

転がり軸受のオイル潤滑に際し、特許文献１においては、一対の転がり軸受が嵌合された筒状のホルダにオイルジェット孔を設け、そのオイルジェット孔から転がり軸受内に潤滑油を噴射して、転がり軸受を潤滑し、冷却している。   In the case of oil lubrication of a rolling bearing, in Patent Document 1, an oil jet hole is provided in a cylindrical holder fitted with a pair of rolling bearings, and lubricating oil is injected into the rolling bearing from the oil jet hole to perform rolling. The bearing is lubricated and cooled.

また、特許文献２においては、玉軸受を支持するオイルフィルムダンパの外部にジェットノズルを設け、そのジェットノズルから玉軸受に向けてオイルを噴射して、玉軸受を潤滑し、冷却している。   Moreover, in patent document 2, a jet nozzle is provided in the exterior of the oil film damper which supports a ball bearing, oil is injected toward the ball bearing from the jet nozzle, the ball bearing is lubricated and cooled.

特開２００９−２６４５２６号公報JP 2009-264526 A 実開昭６２−３５１９５号公報Japanese Utility Model Publication No. 62-35195

ところで、特許文献１および２に記載されたターボチャージャ用軸受装置においては、玉軸受からなる転がり軸受の潤滑に際し、転がり軸受の内輪外径面に向けて潤滑オイルを噴射する構成であり、その噴射方向が転がり軸受の回転方向に対してほぼ直交する方向であるため、潤滑オイルが転動体およびその転動体を保持する保持器の回転により撹拌され、その撹拌により転がり軸受の回転が阻害され、回転抵抗が大きいという不都合がある。   By the way, the turbocharger bearing device described in Patent Documents 1 and 2 is configured to inject lubricating oil toward the inner ring outer diameter surface of the rolling bearing when lubricating the rolling bearing including the ball bearing. Since the direction is substantially perpendicular to the rotation direction of the rolling bearing, the lubricating oil is agitated by the rotation of the rolling elements and the cage that holds the rolling elements, and the agitation impedes the rotation of the rolling bearings, causing rotation. There is a disadvantage that the resistance is large.

この発明の課題は、タービン軸を回転自在に支持する転がり軸受が潤滑オイルによって回転が阻害されるのを抑制することができるようにしたターボチャージャ用軸受装置を提供することである。   An object of the present invention is to provide a turbocharger bearing device that can suppress the rotation of a rolling bearing that rotatably supports a turbine shaft from being inhibited by lubricating oil.

上記の課題を解決するため、この発明においては、筒状の軸受ケースの両端部内に一対の転がり軸受を組み込み、その一対の転がり軸受によってタービン軸を回転自在に支持するターボチャージャ用軸受装置において、前記軸受ケースの内周両端部に転がり軸受の外輪を軸方向に位置決めする環状突出部を設け、その環状突出部の内周に、相反する方向に傾斜する一対のテーパ面を軸方向の両側に有し、その一対のテーパ面の交差部に滑らかな曲面が設けられた断面Ｖ字状の周溝を設け、前記軸受ケースの両端部には外径面および転がり軸受から離れる側のインナ側テーパ面で開口して周溝内に軸受潤滑用オイルを供給する径方向の給油孔を設けた構成を採用したのである。   In order to solve the above problems, in the present invention, in a turbocharger bearing device in which a pair of rolling bearings are incorporated in both ends of a cylindrical bearing case, and the turbine shaft is rotatably supported by the pair of rolling bearings, An annular projection for positioning the outer ring of the rolling bearing in the axial direction is provided at both inner circumferential ends of the bearing case, and a pair of tapered surfaces inclined in opposite directions are provided on both sides in the axial direction on the inner circumference of the annular projection. A circumferential groove having a V-shaped cross section provided with a smooth curved surface at the intersection of the pair of tapered surfaces, and an inner taper on the side away from the outer diameter surface and the rolling bearing at both ends of the bearing case. A configuration in which a radial oil supply hole that opens at the surface and supplies bearing lubrication oil is provided in the circumferential groove is employed.

上記の構成からなるターボチャージャ用軸受装置において、軸受ケースの両端部に設けられた給油孔のそれぞれにオイルを供給すると、そのオイルは一対の転がり軸受により支持されたタービン軸の外周に向けて噴射され、そのタービン軸の回転により周方向に弾き飛ばされて周溝内で旋回し、インナ側テーパ面の傾斜に沿って径方向外方に向けて移動する。   In the turbocharger bearing device configured as described above, when oil is supplied to each of the oil supply holes provided at both ends of the bearing case, the oil is injected toward the outer periphery of the turbine shaft supported by the pair of rolling bearings. Then, it is blown off in the circumferential direction by the rotation of the turbine shaft, turns in the circumferential groove, and moves radially outward along the inclination of the inner tapered surface.

また、オイルがインナ側テーパ面の大径端に連続する曲面に至ると、その曲面およびその曲面に連設されたアウタ側のテーパ面に沿って径方向内方に向けて移動し、旋回しつつ転がり軸受の側面における周方向全体から内部に浸入して転がり軸受を潤滑し、冷却する。   When the oil reaches a curved surface that continues to the large-diameter end of the inner tapered surface, the oil moves radially inward along the curved surface and the outer tapered surface connected to the curved surface. However, the rolling bearing is lubricated and cooled by entering the inside from the entire circumferential direction on the side surface of the rolling bearing.

このように、潤滑用オイルは旋回しつつ転がり軸受内に浸入するため、浸入オイルが転がり軸受で撹拌されることは少ない。そのため、オイルによって転がり軸受の回転が阻害されることも少なくなり、回転抵抗の低減化を図る状態で転がり軸受を効果的に潤滑することができる。   In this way, since the lubricating oil enters the rolling bearing while turning, the intruding oil is rarely agitated by the rolling bearing. Therefore, the rotation of the rolling bearing is less likely to be inhibited by oil, and the rolling bearing can be effectively lubricated in a state where the rotational resistance is reduced.

また、転がり軸受内に浸入したオイルは旋回しつつ流出するため、オイルの入れ換わりが速く、転がり軸受を効果的に冷却することができる。   Further, since the oil that has entered the rolling bearing flows while turning, the oil can be quickly exchanged, and the rolling bearing can be effectively cooled.

ここで、給油孔を、周方向に傾斜してタービン軸の回転方向に向けてオイルを噴射する傾斜状の孔とし、あるいは、軸方向に向けて傾斜して転がり軸受に向けてオイルを噴射する傾斜状の孔とすると、周溝内においてオイルをスムーズに旋回させることができる。   Here, the oil supply holes are inclined holes that incline in the circumferential direction and inject oil toward the rotation direction of the turbine shaft, or incline in the axial direction and inject oil toward the rolling bearing. When the hole is inclined, the oil can be smoothly turned in the circumferential groove.

また、給油孔を、周方向および軸方向の２方向に向けて傾斜して転がり軸受に向けて螺旋状にオイルを噴射する２軸傾斜の傾斜状孔とすると、周溝内においてオイルをよりスムーズに旋回させることができる。   Further, when the oil supply hole is a two-axis inclined inclined hole that inclines in two directions, ie, the circumferential direction and the axial direction, and injects the oil spirally toward the rolling bearing, the oil is smoothed in the circumferential groove. Can be swiveled.

さらに、周溝の内周面にオイルを案内するスパイラル状の微小溝を設けることにより、微小溝に沿ってオイルが流れるため、この場合においてもオイルをよりスムーズに旋回させることができる。   Furthermore, since the oil flows along the minute groove by providing the spiral minute groove for guiding the oil on the inner peripheral surface of the circumferential groove, the oil can be swirled more smoothly even in this case.

また、タービン軸の外径面に転がり軸受の内輪を軸方向に位置決めするスリーブを嵌合し、そのスリーブの外周に、前記給油孔の油出口からアウタ側に片寄った位置でインナ側テーパ面との間に環状の間隙を形成するフランジを設けることにより、周溝内におけるオイルの流速を速め、転がり軸受内に多くのオイルを供給することができ、転がり軸受を効果的に潤滑し、かつ、冷却することができる。   Further, a sleeve for axially positioning the inner ring of the rolling bearing is fitted to the outer diameter surface of the turbine shaft, and an inner side tapered surface is arranged on the outer periphery of the sleeve at a position offset from the oil outlet of the oil supply hole to the outer side. By providing a flange that forms an annular gap between them, the oil flow rate in the circumferential groove can be increased, a large amount of oil can be supplied into the rolling bearing, the rolling bearing is effectively lubricated, and Can be cooled.

この場合、フランジの外周にインナ側テーパ面と同方向に傾斜するテーパ面を設け、そのテーパ面にオイルを案内するスパイラル状の微小溝を設けることにより、周溝内におけるオイルの流速を速めることができ、転がり軸受をより効果的に潤滑し、かつ、冷却することができる。   In this case, by providing a tapered surface inclined in the same direction as the inner tapered surface on the outer periphery of the flange, and providing a spiral minute groove for guiding oil on the tapered surface, the oil flow rate in the circumferential groove can be increased. Thus, the rolling bearing can be more effectively lubricated and cooled.

この発明においては、上記のように、転がり軸受内にオイルを旋回流入させることができるため、転がり軸受が潤滑オイルによって回転阻害されることが少なくなり、回転抵抗の低減化を図る状態で転がり軸受を効果的に潤滑することができる。   In the present invention, as described above, since the oil can be swirled into the rolling bearing, the rolling bearing is less likely to be prevented from rotating by the lubricating oil, and the rolling bearing is in a state where the rotational resistance is reduced. Can be effectively lubricated.

また、転がり軸受内に浸入したオイルをスムーズに排油することができるため、オイルの入れ換わりが速く、転がり軸受を効果的に冷却することができる。   In addition, since the oil that has entered the rolling bearing can be smoothly drained, the oil can be replaced quickly and the rolling bearing can be effectively cooled.

この発明に係るターボチャージャ用軸受装置の実施の形態を示す縦断面図The longitudinal cross-sectional view which shows embodiment of the bearing apparatus for turbochargers which concerns on this invention 図１の一部を拡大して示す断面図Sectional drawing which expands and shows a part of FIG. 図２のIII−III線に沿った断面図Sectional view along line III-III in FIG. 図２のIV−IV線に沿った断面図Sectional view along line IV-IV in FIG. 図２のV−V線に沿った断面図Sectional view along line VV in FIG. 給油孔の他の例を示す断面図Sectional drawing which shows other examples of oil supply hole 給油孔のさらに他の例を示す断面図Sectional view showing still another example of the oil supply hole この発明に係るターボチャージャ用軸受装置の他の実施の形態を示す縦断面図The longitudinal cross-sectional view which shows other embodiment of the bearing apparatus for turbochargers which concerns on this invention 図８の一部を拡大して示す断面図Sectional drawing which expands and shows a part of FIG. 図９に示すフランジの他の例を示す断面図Sectional drawing which shows the other example of the flange shown in FIG. 図１０に示すフランジの一部を示す平面図The top view which shows a part of flange shown in FIG.

以下、この発明の実施の形態を図面に基づいて説明する。図１に示すように、筒状の軸受ケース１０の両端部内周にはタービン軸２０を回転自在に支持する一対の転がり軸受３０が嵌合されている。   Hereinafter, embodiments of the present invention will be described with reference to the drawings. As shown in FIG. 1, a pair of rolling bearings 30 that rotatably support the turbine shaft 20 are fitted to the inner periphery of both ends of a cylindrical bearing case 10.

タービン軸２０の一端部にはタービンホイール２１が取り付けられている。タービンホイール２１は排気ガスによって回転され、そのタービンホイール２１と共にタービン軸２０が回転し、他端部に取り付けられたコンプレッサホイール２２も同方向に回転する。   A turbine wheel 21 is attached to one end of the turbine shaft 20. The turbine wheel 21 is rotated by the exhaust gas, the turbine shaft 20 rotates together with the turbine wheel 21, and the compressor wheel 22 attached to the other end also rotates in the same direction.

転がり軸受３０は、外輪３１と内輪３２との間に転動体としてのボール３３を組み込み、そのボール３３を保持器３４で保持した玉軸受からなる。一対の転がり軸受３０の内輪３２間には、その内輪３２の対向間隔を規制する筒状のスリーブ３５が組み込まれている。スリーブ３５はタービン軸２０に嵌合されて回り止めされ、タービン軸２０と一体に回転する。   The rolling bearing 30 is a ball bearing in which a ball 33 as a rolling element is incorporated between an outer ring 31 and an inner ring 32 and the ball 33 is held by a cage 34. Between the inner rings 32 of the pair of rolling bearings 30, a cylindrical sleeve 35 that restricts the facing distance between the inner rings 32 is incorporated. The sleeve 35 is fitted to the turbine shaft 20 and prevented from rotating, and rotates integrally with the turbine shaft 20.

軸受ケース１０の内周における両端部には一対の転がり軸受３０の外輪３１のそれぞれを軸方向に位置決めする一対の環状突出部１１が設けられ、それぞれの環状突出部１１の内周に周溝１２が設けられている。   A pair of annular protrusions 11 for positioning each of the outer rings 31 of the pair of rolling bearings 30 in the axial direction are provided at both ends of the inner periphery of the bearing case 10, and a circumferential groove 12 is formed on the inner periphery of each annular protrusion 11. Is provided.

図２に示すように、周溝１２は断面Ｖ字状とされ、その内周には相反する方向に傾斜する一対のテーパ面１２ａ、１２ｂが軸方向の両側に設けられ、その一対のテーパ面１２ａ、１２ｂが交差する部分に滑らかな曲面１２ｃが設けられている。   As shown in FIG. 2, the circumferential groove 12 has a V-shaped cross section, and a pair of tapered surfaces 12 a and 12 b inclined in opposite directions are provided on the inner circumference on both sides in the axial direction. A smooth curved surface 12c is provided at a portion where 12a and 12b intersect.

一対のテーパ面１２ａ、１２ｂのうち、転がり軸受３０に近接するアウタ側テーパ面１２ａの小径端における内径は外輪３１の内径より小径で、内輪３２の外径より大径とされている。一方、転がり軸受３０から離れる側のインナ側テーパ面１２ｂの小径端の内径はアウタ側テーパ面１２ａの小径端における内径より小径とされてスリーブ３５の外径面間に微小な間隙１３が設けられている。   Of the pair of tapered surfaces 12 a and 12 b, the inner diameter at the small diameter end of the outer side tapered surface 12 a adjacent to the rolling bearing 30 is smaller than the inner diameter of the outer ring 31 and larger than the outer diameter of the inner ring 32. On the other hand, the inner diameter of the inner diameter tapered surface 12b on the side away from the rolling bearing 30 is smaller than the inner diameter of the outer diameter taper surface 12a, and a minute gap 13 is provided between the outer diameter surfaces of the sleeve 35. ing.

図１乃至図３に示すように、軸受ケース１０の両端部には径方向の給油孔１４が設けられており、その給油孔１４は軸受ケース１０の外径面およびインナ側テーパ面１２ｂの小径側端部で開口している。   As shown in FIGS. 1 to 3, radial oil supply holes 14 are provided at both ends of the bearing case 10, and the oil supply holes 14 have a small diameter of the outer diameter surface of the bearing case 10 and the inner tapered surface 12 b. Opened at the side edge.

実施の形態で示すターボチャージャ用軸受装置は上記の構造からなり、タービン軸２０およびスリーブ３５が、図３の矢印で示す方向に回転する状態において、給油孔１４にオイルを供給すると、そのオイルはタービン軸２０に嵌合されたスリーブ３５の外周に向けて噴射され、そのスリーブ３５の回転により周方向に弾き飛ばされて周溝１２内を旋回し、インナ側テーパ面１２ｂの傾斜に沿って径方向外方に向けて移動する。   The turbocharger bearing device shown in the embodiment has the above structure. When the turbine shaft 20 and the sleeve 35 rotate in the direction indicated by the arrow in FIG. It is injected toward the outer periphery of the sleeve 35 fitted to the turbine shaft 20, is blown off in the circumferential direction by the rotation of the sleeve 35, turns inside the circumferential groove 12, and has a diameter along the inclination of the inner tapered surface 12 b. Move outward in the direction.

上記オイルがインナ側テーパ面１２ｂの大径端に連続する曲面１２ｃに至ると、その曲面１２ｃおよびその曲面１２ｃに連設されたアウタ側テーパ面１２ａに沿って径方向内方に向けて移動し、上記アウタ側テーパ面１２ａにおける小径端の周方向全体から転がり軸受３０内に旋回浸入する。その浸入オイルにより転がり軸受３０は潤滑され、冷却される。   When the oil reaches the curved surface 12c continuous with the large-diameter end of the inner tapered surface 12b, the oil moves inward in the radial direction along the curved surface 12c and the outer tapered surface 12a connected to the curved surface 12c. Rotatingly enters the rolling bearing 30 from the entire circumferential direction of the small diameter end of the outer side tapered surface 12a. The rolling bearing 30 is lubricated and cooled by the infiltrated oil.

このように、潤滑用オイルは旋回しつつ転がり軸受３０内に浸入するため、浸入オイルが転がり軸受３０で撹拌されることは少ない。そのため、オイルによって転がり軸受３０の回転が阻害されることも少なくなり、回転抵抗の低減化を図る状態で転がり軸受３０は効果的に潤滑される。   In this way, since the lubricating oil enters the rolling bearing 30 while turning, the intruding oil is rarely agitated by the rolling bearing 30. Therefore, the rotation of the rolling bearing 30 is less likely to be inhibited by the oil, and the rolling bearing 30 is effectively lubricated in a state where the rotational resistance is reduced.

また、潤滑オイルは旋回しつつ転がり軸受３０内から流出するため、オイルの入れ換わりが速く、転がり軸受３０は効果的に冷却される。   Further, since the lubricating oil flows out of the rolling bearing 30 while turning, the oil is quickly replaced, and the rolling bearing 30 is effectively cooled.

図４および図５に示すように、周溝１２のインナ側テーパ面１２ｂからアウタ側テーパ面１２ａに至る内周面の全体にわたってスパイラル状の微小溝１５を設けると、給油孔１４から周溝１２内に供給されたオイルは微小溝１５に案内されつつ周方向に移動するため、オイルをよりスムーズに確実に旋回させることができる。   As shown in FIGS. 4 and 5, when the spiral micro-groove 15 is provided over the entire inner peripheral surface from the inner tapered surface 12 b to the outer tapered surface 12 a of the circumferential groove 12, the oil supply hole 14 to the circumferential groove 12 are provided. Since the oil supplied inside moves in the circumferential direction while being guided by the minute groove 15, the oil can be turned more smoothly and reliably.

図２および図３に示す例においては、給油孔１４を軸受ケース１０の軸心に直交する径方向孔としたが、図６に示すように、周方向に傾斜してスリーブ３５の回転方向に向けてオイルを噴射する傾斜状の孔としてもよい。   In the example shown in FIGS. 2 and 3, the oil supply hole 14 is a radial hole orthogonal to the shaft center of the bearing case 10, but as shown in FIG. It is good also as an inclined hole which injects oil toward.

また、図７に示すように、給油孔１４を軸方向に向けて傾斜して転がり軸受３０に向けてオイルを噴射する傾斜状の孔としてもよい。さらに、図６に示す場合および図７に示す場合と同様に、周方向および軸方向の２方向に傾斜する２軸傾斜の傾斜状の孔としてもよい。   Further, as shown in FIG. 7, the oil supply hole 14 may be an inclined hole that inclines in the axial direction and injects oil toward the rolling bearing 30. Further, similarly to the case shown in FIG. 6 and the case shown in FIG. 7, a biaxially inclined hole inclined in two directions of the circumferential direction and the axial direction may be used.

上記のように、給油孔１４を周方向、軸方向および周方向と軸方向の２方向に傾斜する傾斜孔とすることにより、周溝１２内においてオイルをスムーズに確実に旋回させることができる。   As described above, the oil supply holes 14 are inclined holes that are inclined in the circumferential direction, the axial direction, and the two directions of the circumferential direction and the axial direction, so that the oil can be smoothly and reliably swirled in the circumferential groove 12.

図８および図９は、ターボチャージャ用軸受装置の他の実施の形態を示す。この実施の形態では、スリーブ３５の外周にフランジ３６を設けている点で図１および図２に示す軸受装置と相違する。   8 and 9 show another embodiment of the turbocharger bearing device. This embodiment is different from the bearing device shown in FIGS. 1 and 2 in that a flange 36 is provided on the outer periphery of the sleeve 35.

ここで、フランジ３６は、周溝１２のインナ側テーパ面１２ｂと対向する部位に設けられていると共に、給油孔１４からアウタ側に片寄った位置に設けられている。また、フランジ３６の外周にはインナ側テーパ面１２ｂと同方向に傾斜するテーパ面３７を設けられ、このテーパ面３７とインナ側テーパ面１２ｂとの間で円錐形の間隙３８が形成されている。   Here, the flange 36 is provided at a portion facing the inner taper surface 12b of the circumferential groove 12, and is provided at a position offset from the oil supply hole 14 toward the outer side. Further, a tapered surface 37 inclined in the same direction as the inner tapered surface 12b is provided on the outer periphery of the flange 36, and a conical gap 38 is formed between the tapered surface 37 and the inner tapered surface 12b. .

上記のように、スリーブ３５にフランジ３６を設け、そのフランジ３６の外周にインナ側テーパ面１２ｂとの間で円錐形の間隙３８を形成するテーパ面３７を設けることにより、給油孔１４から周溝１２内に供給されたオイルの流速を速め、転がり軸受３０内に多くのオイルを供給することができることになり、転がり軸受３０を効果的に潤滑し、かつ、冷却することができる。   As described above, the flange 35 is provided on the sleeve 35, and the tapered surface 37 that forms the conical gap 38 between the flange 36 and the inner tapered surface 12b is provided on the outer periphery of the flange 36. Accordingly, the flow rate of the oil supplied into the cylinder 12 can be increased, and a large amount of oil can be supplied into the rolling bearing 30, so that the rolling bearing 30 can be effectively lubricated and cooled.

ここで、図１０および図１１に示すように、フランジ３６の外周テーパ面３７
にオイルを案内するスパイラル状の複数の微小溝３９を周方向に間隔をおいて設けることにより、周溝１２内におけるオイルの流速さらに高めることができ、転がり軸受３０をより効果的に潤滑し、かつ、冷却することができる。 Here, as shown in FIGS. 10 and 11, the outer peripheral tapered surface 37 of the flange 36.
By providing a plurality of spiral micro-grooves 39 for guiding oil in the circumferential direction, the oil flow rate in the circumferential groove 12 can be further increased, and the rolling bearing 30 can be more effectively lubricated, And it can be cooled.

１０ 軸受ケース
１１ 環状突出部
１２ 周溝
１２ａ アウタ側テーパ面
１２ｂ インナ側テーパ面
１２ｃ 曲面
１３ 間隙
１４ 給油孔
１５ 微小溝
２０ タービン軸
３０ 転がり軸受
３１ 外輪
３２ 内輪
３５ スリーブ
３６ フランジ
３７ テーパ面
３８ 間隙
３９ 微小溝 10 bearing case 11 annular protrusion 12 circumferential groove 12a outer taper surface 12b inner taper surface 12c curved surface 13 gap 14 oil supply hole 15 minute groove 20 turbine shaft 30 rolling bearing 31 outer ring 32 inner ring 35 sleeve 36 flange 37 taper surface 38 gap 39 Micro groove

Claims (8)

筒状の軸受ケース（１０）の両端部内に一対の転がり軸受（３０）を組み込み、その一対の転がり軸受（３０）によってタービン軸（２０）を回転自在に支持するターボチャージャ用軸受装置において、
前記軸受ケース（１０）の内周両端部に転がり軸受（３０）の外輪（３１）を軸方向に位置決めする環状突出部（１１）を設け、その環状突出部（１１）の内周に、相反する方向に傾斜する一対のテーパ面（１２ａ、１２ｂ）を軸方向の両側に有し、その一対のテーパ面（１２ａ、１２ｂ）の交差部に滑らかな曲面（１２ｃ）が設けられた断面Ｖ字状の周溝（１２）を設け、前記軸受ケース（１０）の両端部には外径面および転がり軸受（３０）から離れる側のインナ側テーパ面（１２ｂ）で開口して周溝（１２）内に軸受潤滑用オイルを供給する径方向の給油孔（１４）を設けたことを特徴とするターボチャージャ用軸受装置。 In a turbocharger bearing device in which a pair of rolling bearings (30) is incorporated in both ends of a cylindrical bearing case (10), and the turbine shaft (20) is rotatably supported by the pair of rolling bearings (30).
An annular protrusion (11) for positioning the outer ring (31) of the rolling bearing (30) in the axial direction is provided at both inner peripheral ends of the bearing case (10), and a reciprocal is provided on the inner periphery of the annular protrusion (11). Having a pair of tapered surfaces (12a, 12b) that are inclined in the direction in which the pair of taper surfaces (12a, 12b) are provided on both sides in the axial direction, and a smooth curved surface (12c) is provided at the intersection of the pair of tapered surfaces (12a, 12b). A circumferential groove (12) is provided, and both ends of the bearing case (10) are opened by an outer diameter surface and an inner taper surface (12b) on the side away from the rolling bearing (30). A turbocharger bearing device comprising a radial oil supply hole (14) for supplying bearing lubricating oil therein. 前記給油孔（１４）が、周方向に傾斜して前記タービン軸（２０）の回転方向に向けてオイルを噴射する傾斜状の孔からなる請求項１に記載のターボチャージャ用軸受装置。   2. The turbocharger bearing device according to claim 1, wherein the oil supply hole is an inclined hole that inclines in a circumferential direction and injects oil toward a rotation direction of the turbine shaft. 前記給油孔（１４）が、軸方向に向けて傾斜して前記転がり軸受（３０）に向けてオイルを噴射する傾斜状の孔からなる請求項１に記載のターボチャージャ用軸受装置。   The turbocharger bearing device according to claim 1, wherein the oil supply hole (14) is an inclined hole that inclines toward the axial direction and injects oil toward the rolling bearing (30). 前記給油孔（１４）が、周方向および軸方向の２方向に向けて傾斜して転がり軸受に向けて螺旋状にオイルを噴射する２軸傾斜の傾斜状孔からなる請求項１に記載のターボチャージャ用軸受装置。   The turbo according to claim 1, wherein the oil supply hole (14) includes a biaxially inclined inclined hole that inclines toward two directions of a circumferential direction and an axial direction and injects oil spirally toward a rolling bearing. Charger bearing device. 前記周溝（１２）の内周面にオイルを案内するスパイラル状の微小溝（１５）を設けた請求項１乃至４のいずれか１項に記載のターボチャージャ用軸受装置。   The turbocharger bearing device according to any one of claims 1 to 4, wherein a spiral minute groove (15) for guiding oil is provided on an inner circumferential surface of the circumferential groove (12). 前記タービン軸（２０）の外径面に前記転がり軸受（３０）の内輪（３２）を軸方向に位置決めするスリーブ（３５）を嵌合し、そのスリーブ（３５）の外周に、前記給油孔（１４）の油出口からアウタ側に片寄った位置でインナ側テーパ面（１２ｂ）との間に環状の間隙（３８）を形成するフランジ（３６）を設けた請求項１乃至５のいずれか１項に記載のターボチャージャ用軸受装置。   A sleeve (35) for axially positioning the inner ring (32) of the rolling bearing (30) is fitted to the outer diameter surface of the turbine shaft (20), and the oil supply hole ( The flange (36) which forms an annular gap (38) between the inner side taper surface (12b) at a position offset from the oil outlet to the outer side in (14). The bearing device for turbochargers described in 1. 前記フランジ（３６）の外周に前記インナ側テーパ面（１２ｂ）と同方向に傾斜するテーパ面（３７）を設けた請求項６に記載のターボチャージャ用軸受装置。   The turbocharger bearing device according to claim 6, wherein a tapered surface (37) inclined in the same direction as the inner tapered surface (12b) is provided on an outer periphery of the flange (36). 前記フランジ（３６）の外周のテーパ面（３７）にオイルを案内するスパイラル状の微小溝（３９）を設けた請求項７に記載のターボチャージャ用軸受装置。   The turbocharger bearing device according to claim 7, wherein spiral tapered grooves (39) for guiding oil are provided on a tapered surface (37) on an outer periphery of the flange (36).
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