JP2003166537A - Thrust bearing unit for turbocharger - Google Patents

Thrust bearing unit for turbocharger

Info

Publication number
JP2003166537A
JP2003166537A JP2001363401A JP2001363401A JP2003166537A JP 2003166537 A JP2003166537 A JP 2003166537A JP 2001363401 A JP2001363401 A JP 2001363401A JP 2001363401 A JP2001363401 A JP 2001363401A JP 2003166537 A JP2003166537 A JP 2003166537A
Authority
JP
Japan
Prior art keywords
thrust
thrust bearing
lubricating oil
runner
thrust runner
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Pending
Application number
JP2001363401A
Other languages
Japanese (ja)
Inventor
Makoto Henmi
真 辺見
Atsushi Houkida
淳 伯耆田
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Hitachi Ltd
Original Assignee
Hitachi Ltd
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Hitachi Ltd filed Critical Hitachi Ltd
Priority to JP2001363401A priority Critical patent/JP2003166537A/en
Publication of JP2003166537A publication Critical patent/JP2003166537A/en
Pending legal-status Critical Current

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C17/00—Sliding-contact bearings for exclusively rotary movement
    • F16C17/04—Sliding-contact bearings for exclusively rotary movement for axial load only
    • F16C17/047—Sliding-contact bearings for exclusively rotary movement for axial load only with fixed wedges to generate hydrodynamic pressure
    • 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
    • F16C33/02—Parts of sliding-contact bearings
    • F16C33/04—Brasses; Bushes; Linings
    • F16C33/06—Sliding surface mainly made of metal
    • F16C33/10—Construction relative to lubrication
    • F16C33/1025—Construction relative to lubrication with liquid, e.g. oil, as lubricant
    • F16C33/1045—Details of supply of the liquid to the bearing
    • 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
    • F16C33/02—Parts of sliding-contact bearings
    • F16C33/04—Brasses; Bushes; Linings
    • F16C33/06—Sliding surface mainly made of metal
    • F16C33/10—Construction relative to lubrication
    • F16C33/1025—Construction relative to lubrication with liquid, e.g. oil, as lubricant
    • F16C33/106—Details of distribution or circulation inside the bearings, e.g. details of the bearing surfaces to affect flow or pressure of the liquid
    • 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

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Chemical & Material Sciences (AREA)
  • Oil, Petroleum & Natural Gas (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Supercharger (AREA)
  • Sliding-Contact Bearings (AREA)

Abstract

<P>PROBLEM TO BE SOLVED: To realize a thrust bearing unit having the least amount and loss of consumed lubricating oil by supplying the lubricating oil from one side of a thrust runner flows out to its other side. <P>SOLUTION: The thrust bearing unit comprises the thrust runner 3 vertically installed to a rotary shaft, and a thrust bearing 2 slidably keeping in contact with one surface of the thrust runner. The other surface of the thrust runner is provided to slidably keep in contact with an end of a radial bearing housing. By providing lubricating oil passage passing through all or a part of a radial direction in a part of a peripheral direction of the thrust runner, the bearing supporting loads of both directions at the least amount of oil is realized in such a way that lubricating oil leaked from the radial bearing is supplied to the opposite side of the thrust runner. <P>COPYRIGHT: (C)2003,JPO

Description

【発明の詳細な説明】Detailed Description of the Invention

【０００１】[0001]

【発明の属する技術分野】本発明はターボチャージャに
使用されるスラスト軸受に関するものである。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a thrust bearing used in a turbocharger.

【０００２】[0002]

【従来の技術】スラストランナは互いに平行な２枚の円
盤により構成され、ロータに垂直に取り付けられてい
る。スラスト軸受は馬蹄形の切り欠きのある円盤であ
り、切り欠き部にロータが入り、２枚のスラストランナ
に挟まれるように組まれる。ロータ回転時には、スラス
ト軸受の両面とスラストランナとが摺動接触することに
よりロータの軸方向変位を抑制する。2. Description of the Related Art A thrust runner is composed of two disks that are parallel to each other and is mounted vertically on a rotor. The thrust bearing is a disc with a horseshoe-shaped notch, and the rotor is inserted into the notch and is assembled so as to be sandwiched between two thrust runners. When the rotor rotates, both surfaces of the thrust bearing and the thrust runner make sliding contact with each other, thereby suppressing axial displacement of the rotor.

【０００３】スラスト軸受とスラストランナとの摺動部
に給油するために、スラスト軸受には給油孔が空けられ
ている。給油孔の一端はオイルポンプに通じる油溜まり
に接続されており、他端はスラスト軸受両面の給油口に
つながっている。An oil supply hole is formed in the thrust bearing in order to supply oil to the sliding portion between the thrust bearing and the thrust runner. One end of the oil supply hole is connected to an oil reservoir leading to the oil pump, and the other end is connected to the oil supply ports on both sides of the thrust bearing.

【０００４】[0004]

【発明が解決しようとする課題】このようなスラスト軸
受においては、給油口がスラスト軸受の両面に設けられ
ている。したがって、軸方向力を支える側の摺動面だけ
でなく反対側の摺動面にも不必要な給油がされることに
なり、過剰に給油された潤滑油による攪拌損失が大きく
なるなどの問題があった。また、給油孔は細く長いた
め、加工が困難であり、コスト高を招くという問題もあ
った。本発明はかかる点に鑑みて、給油口を片側に設け
るという簡単な構成でスラストランナ両面の摺動面の潤
滑がなされるようにすることを目的とする。In such a thrust bearing, the oil supply ports are provided on both sides of the thrust bearing. Therefore, unnecessary lubrication is applied not only to the sliding surface that supports the axial force but also to the sliding surface on the opposite side, and problems such as increased agitation loss due to excessively lubricated lubricating oil was there. Further, since the oil supply hole is thin and long, it is difficult to process the oil supply hole, which causes a problem of high cost. In view of the above point, the present invention has an object to lubricate the sliding surfaces on both sides of the thrust runner with a simple structure in which the oil supply port is provided on one side.

【０００５】[0005]

【課題を解決するための手段】本発明においては、その
回転軸に垂直に取り付けられたスラストランナと，その
スラストランナの一方の面に摺動接触するスラスト軸受
とからなり，前記スラストランナの他方の面はラジアル
軸受ハウジングの端部と摺動接触するように構成された
スラスト軸受装置において，前記スラストランナの円周
方向の一部において，半径方向のすべてまたは一部を貫
通させることにより課題を解決するものである。すなわ
ち、本発明は、スラストランナの一方の面と他方の面と
の間に、両面に連通（貫通）する潤滑油路を形成した。According to the present invention, there is provided a thrust runner vertically attached to the rotating shaft of the thrust runner and a thrust bearing slidably contacting one surface of the thrust runner. In a thrust bearing device configured so that the surface of the thrust bearing device is in sliding contact with the end of the radial bearing housing, the problem is solved by penetrating all or part of the radial direction in a part of the thrust runner in the circumferential direction. It is a solution. That is, according to the present invention, a lubricating oil passage communicating (penetrating) with both surfaces is formed between one surface and the other surface of the thrust runner.

【０００６】[0006]

【発明の実施の形態】以下、図面を参照し、本発明の実
施の形態１について説明する。図１は，本発明に掛かる
ターボチャージャ用スラスト軸受装置の断面図、図２
は、図１のＡ−Ａ断面図の１例，図３は図１のＡ−Ａ断
面図のもうひとつの例である。図４は本発明に掛かるタ
ーボチャージャ用スラスト軸受装置を用いたターボチャ
ージャの断面図である。BEST MODE FOR CARRYING OUT THE INVENTION Embodiment 1 of the present invention will be described below with reference to the drawings. FIG. 1 is a sectional view of a thrust bearing device for a turbocharger according to the present invention, and FIG.
1 is an example of the AA sectional view of FIG. 1, and FIG. 3 is another example of the AA sectional view of FIG. FIG. 4 is a sectional view of a turbocharger using the thrust bearing device for a turbocharger according to the present invention.

【０００７】図４に示すように、軸受ハウジング４内に
収容された回転軸１の右端にはタービン翼車３０が取り
付けられており、図示されないエンジンの排気ガスがこ
のタービン翼車３０に吹き付けられることにより、回転
軸１は回転する。回転軸１の左端にはコンプレッサイン
ペラー３１が取り付けられており、このコンプレッサイ
ンペラー３１の回転により空気または空気と燃料の混合
気が圧縮され、図示されないエンジンに供給される。As shown in FIG. 4, a turbine impeller 30 is attached to the right end of the rotary shaft 1 housed in the bearing housing 4, and exhaust gas of an engine (not shown) is blown to the turbine impeller 30. As a result, the rotary shaft 1 rotates. A compressor impeller 31 is attached to the left end of the rotary shaft 1, and the rotation of the compressor impeller 31 compresses air or a mixture of air and fuel and supplies the compressed air to an engine (not shown).

【０００８】回転軸１は浮動ブッシュ軸受５ａ、５ｂに
より回転可能に支持され、ラジアル方向の変位が抑えら
れている。なお、外部で昇圧された潤滑油はラジアル軸
受給油孔６から給油口をとおり浮動ブッシュ軸受５ａ、
５ｂに供給される。また、回転軸１にはスラストランナ
３が嵌合され、このスラストランナ３はラジアル軸受ハ
ウジング４とスラスト軸受２とともに本発明のスラスト
軸受装置を構成している。図中、８ａ、８ｂは浮動ブッ
シュ軸受５ａ、５ｂの軸方向の移動を抑制する止めリン
グである。The rotating shaft 1 is rotatably supported by the floating bush bearings 5a and 5b, and its displacement in the radial direction is suppressed. In addition, the lubricating oil pressurized outside is passed from the radial bearing oil supply hole 6 through the oil supply port to the floating bush bearing 5a,
5b. A thrust runner 3 is fitted on the rotary shaft 1, and the thrust runner 3 constitutes a thrust bearing device of the present invention together with the radial bearing housing 4 and the thrust bearing 2. In the figure, 8a and 8b are stop rings for suppressing the axial movement of the floating bush bearings 5a and 5b.

【０００９】図１に示すように、回転軸１は半径方向を
浮動ブッシュ軸受５により支持されており、回転軸１に
取り付けられたスラストランナ２をスラスト軸受２およ
びラジアル軸受ハウジング４の端面により摺動支持する
ことにより軸方向変位を拘束されている。As shown in FIG. 1, the rotary shaft 1 is supported in the radial direction by a floating bush bearing 5, and a thrust runner 2 mounted on the rotary shaft 1 is slid by the end faces of the thrust bearing 2 and the radial bearing housing 4. Axial displacement is restricted by the dynamic support.

【００１０】回転軸がタービン側（右方）に引かれる場
合、スラストランナ３とハウジング４の端部とが摺動接
触する。ラジアル軸受給油孔６をとおり、ラジアル軸受
である浮動ブッシュ５の外周側のすきまに給油された潤
滑油のうち、余剰分はすきまから軸方向に流出する。ス
ラスト軸受側に流出した潤滑油は、スラストランナ３に
接触すると、スラストランナ３の回転に伴う遠心力によ
り外周側に押し出される。このようにして流れ込んだ潤
滑油によりスラストランナ３とハウジング４との間の摺
動面は潤滑される。When the rotary shaft is pulled to the turbine side (right side), the thrust runner 3 and the end of the housing 4 make sliding contact. Through the radial bearing oil supply hole 6, of the lubricating oil supplied to the clearance on the outer peripheral side of the floating bush 5 which is the radial bearing, the surplus oil flows out from the clearance in the axial direction. When the lubricating oil flowing out to the thrust bearing side comes into contact with the thrust runner 3, the lubricating oil is pushed out to the outer peripheral side by the centrifugal force accompanying the rotation of the thrust runner 3. The lubricating oil thus flowed in lubricates the sliding surface between the thrust runner 3 and the housing 4.

【００１１】回転軸がコンプレッサ側（左方）に引かれ
る場合、スラストランナ３とスラスト軸受２とが摺動接
触する。本実施例によれば、図２に示すように、スラス
トランナ３は円周方向の６箇所において摺動接触部分９
の半径方向すべてにわたり貫通するように切り欠き１０
が設けられ、切り欠き部１１が形成されている。摺動接
触部分９はほぼ突起状の四角形をなし、切り欠き部１１
はほぼ一方が開放された三角形をなす。図１において、
摺動接触部分９とスラスト軸受２とが接触する面の中心
を通る線を中心線Ｍとしたときに、図２において切り欠
き１０の底部３１は中心線Ｍの内側（中心側）にある。
これは中心側を貫通して流れた潤滑油を遠心力によって
外側に流し、摺動接触面全体に潤滑油がいき渡るように
するためである。以上のように、浮動ブッシュ５の外周
側からスラスト軸受側に流れ出た潤滑油の一部は、これ
らの切り欠きを通り抜けてスラストランナ３とスラスト
軸受２との摺動接触面を潤滑することができる。また、
切り欠き部１１は面積が大きくされ、その分だけ摺動接
触面を小さくすることができる。When the rotary shaft is pulled to the compressor side (left side), the thrust runner 3 and the thrust bearing 2 make sliding contact. According to this embodiment, as shown in FIG. 2, the thrust runner 3 has sliding contact portions 9 at six positions in the circumferential direction.
Notch 10 to penetrate all over the radial direction of
Is provided, and the notch 11 is formed. The sliding contact portion 9 has a substantially protruding square shape, and the cutout portion 11
Has a triangular shape with one side open. In FIG.
When the line passing through the center of the surface where the sliding contact portion 9 and the thrust bearing 2 contact each other is taken as the center line M, the bottom portion 31 of the notch 10 is inside (center side) of the center line M in FIG.
This is because the lubricating oil flowing through the center side is caused to flow to the outside by the centrifugal force so that the lubricating oil spreads over the entire sliding contact surface. As described above, a part of the lubricating oil flowing out from the outer peripheral side of the floating bush 5 to the thrust bearing side can pass through these notches and lubricate the sliding contact surface between the thrust runner 3 and the thrust bearing 2. it can. Also,
The notch 11 has a large area, and the sliding contact surface can be made smaller accordingly.

【００１２】スラストランナ３に設ける貫通部分である
孔３２を備えた孔部３３は、図３に示すように半径方向
の一部のみとなるような形状でも良い。この場合にあっ
ても、孔３２は、全部あるいはそのほとんどが中心線Ｍ
の内側に存在する。このように貫通部分を形成すると、
貫通部分の外周側にも摺動接触面が形成されるが、この
部分には遠心力により潤滑油が押し出されやすいので、
摺動接触面へ潤滑油が行き渡りやすくなる。The hole portion 33 provided with the hole 32, which is a penetrating portion, provided in the thrust runner 3 may be shaped so as to form only a part in the radial direction as shown in FIG. Even in this case, all or most of the holes 32 are center lines M.
Exists inside. When the penetrating portion is formed in this way,
A sliding contact surface is also formed on the outer peripheral side of the penetrating part, but since lubricating oil is easily pushed out by this part due to centrifugal force,
Lubricating oil can easily spread to the sliding contact surface.

【００１３】本実施例のような貫通部分が設けられてい
ない場合、浮動ブッシュ５の外周側からスラスト軸受側
に流れ出た潤滑油はすべて、スラストランナ３とハウジ
ング４との間の摺動面をとおりスラストランナ３の外周
に流れ出してしまう。一度スラストランナ３の外周まで
流れ出てしまった潤滑油は、スラストランナ３の回転に
よる遠心力に抗ってスラストランナ３とスラスト軸受２
の間の摺動面に入り込みにくいため、この摺動面への潤
滑油の供給はあまり期待できない。このため、スラスト
軸受２とスラストランナ３との摺動面へ潤滑油を供給す
るための給油孔をスラスト軸受２の内部に、別途設ける
必要があった。In the case where the penetrating portion as in this embodiment is not provided, all the lubricating oil flowing out from the outer peripheral side of the floating bush 5 to the thrust bearing side flows on the sliding surface between the thrust runner 3 and the housing 4. As it is, it flows out to the outer periphery of the thrust runner 3. The lubricating oil once flowing out to the outer periphery of the thrust runner 3 resists the centrifugal force caused by the rotation of the thrust runner 3 and the thrust bearing 2 and the thrust bearing 2.
Since it does not easily enter the sliding surface between them, the supply of lubricating oil to this sliding surface cannot be expected so much. For this reason, it is necessary to separately provide an oil supply hole inside the thrust bearing 2 for supplying lubricating oil to the sliding surface between the thrust bearing 2 and the thrust runner 3.

【００１４】これに対し、本実施の形態では、スラスト
ランナ３がハウジング４側からスラスト軸受２側に貫通
しているためにスラスト軸受２側の摺動面にも潤滑油が
流れやすい。したがって、スラスト軸受２とスラストラ
ンナ３との摺動面への給油孔を設ける必要は無くなる。
これにより、スラスト軸受への給油は浮動ブッシュ軸受
の軸方向側面からの漏れによるものだけとなり、スラス
ト軸受のみに別系統から給油する必要は無い。ターボチ
ャージャ全体への給油量は少なく抑えることができるた
め、容量の小さなオイルポンプを使用することが可能と
なる。また、スラスト軸受装置からもれる潤滑油量が少
なくなるため、コンプレッサへの潤滑油の漏れを低減す
ることも可能となる。On the other hand, in this embodiment, since the thrust runner 3 penetrates from the housing 4 side to the thrust bearing 2 side, the lubricating oil easily flows on the sliding surface on the thrust bearing 2 side. Therefore, it is not necessary to provide an oil supply hole in the sliding surface between the thrust bearing 2 and the thrust runner 3.
As a result, oil is only supplied to the thrust bearing by leakage from the axial side surface of the floating bush bearing, and it is not necessary to supply oil only to the thrust bearing from another system. Since the amount of oil supplied to the entire turbocharger can be kept small, it is possible to use an oil pump with a small capacity. Further, since the amount of lubricating oil leaked from the thrust bearing device is reduced, it is possible to reduce the leakage of lubricating oil to the compressor.

【００１５】また、本実施例によれば、スラストランナ
３のハウジング側は固体潤滑剤によりコーティングされ
ている。このようなコーティングが施されていることに
より、スラストランナ３と浮動ブッシュ５との間の摩擦
は小さくなる。したがって、浮動ブッシュ５はスラスト
ランナ３の回転に連れまわりにくくなり、浮動ブッシュ
５の回転数が不必要に大きくなりすぎるために生じる不
安定振動を抑制することが出来る。Further, according to this embodiment, the housing side of the thrust runner 3 is coated with a solid lubricant. By providing such a coating, the friction between the thrust runner 3 and the floating bush 5 is reduced. Therefore, it becomes difficult for the floating bush 5 to follow the rotation of the thrust runner 3, and it is possible to suppress unstable vibration that occurs due to the rotation speed of the floating bush 5 unnecessarily increasing.

【００１６】図５および６は実施の形態２を示し、それ
ぞれ、図５は図２のＢ−Ｂ線，図６は図３のＢ'−Ｂ'線
に沿った断面図である。よって実施の形態１を前提とし
て構成してある。本実施の形態においては、両側のスラ
ストランナの摺動接触面に、円周方向に延びるテーパ部
２０が設けられている。5 and 6 show the second embodiment. FIG. 5 is a sectional view taken along the line BB in FIG. 2 and FIG. 6 is a sectional view taken along the line B'-B 'in FIG. Therefore, the configuration is based on the first embodiment. In the present embodiment, tapered portions 20 extending in the circumferential direction are provided on the sliding contact surfaces of the thrust runners on both sides.

【００１７】図５の例にあっては、テーパ部２０はそれ
ぞれの面がランド部２１とテーパ本体部からなり、図６
の例にあっては、更に貫通部２３（２３ａ，２３ｂ）を
有し、貫通部２３ａ、２３ｂはそれぞれ貫通した孔部３
３、３４が形成される。In the example of FIG. 5, each surface of the taper portion 20 is composed of a land portion 21 and a taper main body portion.
In the example of FIG. 3, the through-holes 23 (23a, 23b) are further provided, and the through-holes 23a, 23b respectively penetrate the hole 3
3, 34 are formed.

【００１８】実施の形態２の効果について以下説明す
る。実施の形態１のような構成では、スラストランナの
摺動面は摺動相手であるハウジング端部やスラスト軸受
と平行であるため、これらにはさまれる油膜は均一では
あるが薄いものとなるおそれがある。しかしながら，こ
のように周方向に均一に薄い油膜では，粘性力が強く効
くために遠心力が相殺され，潤滑油は外周側に押し出さ
れにくくなるおそれがある。本実施例による構成によれ
ば，スラストランナには円周方向に延びるテーパ部が設
けられているため，テーパ部においては油膜は厚くなっ
ている。この油膜の厚い部分においては粘性力の影響は
比較的小さくなるため，潤滑油は外周側にも流れ出しや
すくなって前述したおそれが解決される。The effects of the second embodiment will be described below. In the configuration like the first embodiment, the sliding surface of the thrust runner is parallel to the housing end portion or the thrust bearing, which is a sliding partner, so that the oil film sandwiched between them may be uniform but thin. There is. However, in such an oil film that is evenly thin in the circumferential direction, the viscous force is so strong that the centrifugal force is canceled out, and the lubricating oil may be less likely to be pushed out to the outer peripheral side. According to the configuration of this embodiment, the thrust runner is provided with the taper portion extending in the circumferential direction, so that the oil film is thicker in the taper portion. The influence of the viscous force is relatively small in the thick portion of the oil film, so that the lubricating oil easily flows out to the outer peripheral side and the above-mentioned fear is solved.

【００１９】実施の形態２には，以下のような効果もあ
る。実施の形態１のような構成では、スラストランナの
摺動面は摺動相手であるハウジング端部やスラスト軸受
と平行であるため、これらにはさまれる油膜に動圧は発
生しない。したがって，スラストランナとその摺動相手
面とが直接接触することにより軸方向荷重を支えること
になる。固体面が直接接触するため，摩耗が発生しやす
い。本実施例による構成によれば，スラストランナには
円周方向に延びるテーパ部が設けられているため，スラ
ストランナが回転すると，くさび効果により油膜には動
圧が発生する。油膜に圧力が発生し軸方向荷重の一部は
油膜が受け持つことで，固体面の接触力は小さくなり，
摩耗は発生しにくくなる。以上述べたように、本発明の
ターボチャージャ用スラスト軸受装置によれば、コスト
が低く信頼性の高いターボチャージャを提供することが
可能となる。The second embodiment also has the following effects. In the configuration like the first embodiment, the sliding surface of the thrust runner is parallel to the housing end portion or the thrust bearing that is a sliding partner, so that no dynamic pressure is generated in the oil film sandwiched between them. Therefore, the axial load is supported by direct contact between the thrust runner and its sliding counterpart surface. Wear is likely to occur because the solid surface is in direct contact. According to the configuration of this embodiment, the thrust runner is provided with the taper portion that extends in the circumferential direction. Therefore, when the thrust runner rotates, dynamic pressure is generated in the oil film due to the wedge effect. Since pressure is generated in the oil film and the oil film takes part of the axial load, the contact force on the solid surface becomes smaller,
Wear is less likely to occur. As described above, according to the thrust bearing device for a turbocharger of the present invention, it is possible to provide a turbocharger with low cost and high reliability.

【００２０】[0020]

【発明の効果】上記した本発明のスラスト軸受によれ
ば，浮動ブッシュ５の外周側からスラスト軸受側に流れ
出た潤滑油の一部は、潤滑油路を通り抜けてスラストラ
ンナ３とスラスト軸受２との摺動接触面を潤滑すること
が可能となり、従って給油口が１つであっても両側の摺
動接触面を潤滑することができ、潤滑油消費量の低いタ
ーボチャージャ用スラスト軸受を実現することができ
る。According to the thrust bearing of the present invention described above, a part of the lubricating oil flowing from the outer peripheral side of the floating bush 5 to the thrust bearing side passes through the lubricating oil passage to form the thrust runner 3 and the thrust bearing 2. It is possible to lubricate the sliding contact surfaces of both sides, and therefore, even if there is only one oil supply port, the sliding contact surfaces on both sides can be lubricated, and a thrust bearing for turbocharger with low consumption of lubricating oil is realized. be able to.

【図面の簡単な説明】[Brief description of drawings]

【図１】本発明のターボチャージャ用スラスト軸受装置
の第一の実施形態を示す構成図。FIG. 1 is a configuration diagram showing a first embodiment of a thrust bearing device for a turbocharger of the present invention.

【図２】図１のＡ―Ａ断面図の一例を示す図。2 is a diagram showing an example of a cross-sectional view taken along the line AA of FIG.

【図３】図１のＡ―Ａ断面図のもう一つの例を示す図。FIG. 3 is a diagram showing another example of the AA cross-sectional view of FIG. 1.

【図４】実施例のターボチャージャの断面図。FIG. 4 is a sectional view of a turbocharger according to an embodiment.

【図５】図２のＢ―Ｂ断面図。5 is a sectional view taken along line BB of FIG.

【図６】図３のＢ'―Ｂ'断面図。FIG. 6 is a sectional view taken along the line B′-B ′ of FIG.

【符号の説明】[Explanation of symbols]

１…回転軸，２…スラスト軸受，３…スラストランナ，
４…ラジアル軸受ハウジング，５…浮動ブッシュ軸受，
６…ラジアル軸受給油孔，７…ラジアル軸受ハウジン
グ，８…止めリング，１２…オイル溜り，１３…スラス
ト軸受給油孔，１４…スラスト軸受給油口，２０…テー
パ部、２１…ランド部，２２…テーパ本体部，２３…貫
通部，３０…タービン翼車，４１…コンプレッサインペ
ラー1 ... Rotary shaft, 2 ... Thrust bearing, 3 ... Thrust runner,
4 ... Radial bearing housing, 5 ... Floating bush bearing,
6 ... Radial bearing oil supply hole, 7 ... Radial bearing housing, 8 ... Stop ring, 12 ... Oil sump, 13 ... Thrust bearing oil supply hole, 14 ... Thrust bearing oil supply port, 20 ... Tapered portion, 21 ... Land portion, 22 ... Tapered Body part, 23 ... Penetration part, 30 ... Turbine impeller, 41 ... Compressor impeller

フロントページの続き Ｆターム(参考） 3G005 EA04 EA16 FA41 GB59 3J011 AA06 AA07 BA06 CA01 JA01 KA01 KA03 MA03 MA05 MA27Continued front page    F-term (reference) 3G005 EA04 EA16 FA41 GB59                 3J011 AA06 AA07 BA06 CA01 JA01                       KA01 KA03 MA03 MA05 MA27

Claims (6)

【特許請求の範囲】[Claims] 【請求項１】回転軸に垂直に取り付けられたスラストラ
ンナと、該スラストランナの一方の面に摺動接触するス
ラスト軸受を備え、前記スラストランナは他方の面がラ
ジアル軸受ハウジングの端面と摺動接触するように構成
され、摺動接触する面に潤滑油が供給されるようにした
スラスト軸受装置において、 前記スラストランナの一方の面と他方の面との間に、両
面に連通する潤滑油路を形成したことを特徴とするスラ
スト軸受装置。1. A thrust runner vertically attached to a rotary shaft and a thrust bearing slidingly contacting one surface of the thrust runner, the thrust runner having the other surface sliding on an end surface of a radial bearing housing. A thrust bearing device configured to come into contact with each other and to which lubricating oil is supplied to a sliding contact surface, wherein a lubricating oil passage communicating between both surfaces of the thrust runner is provided. A thrust bearing device characterized by being formed. 【請求項２】請求項１において、前記潤滑油路は、前記
スラストランナに半径方向に外周まで切り欠かれた切り
欠き部によって形成されることを特徴とするスラスト軸
受装置。2. The thrust bearing device according to claim 1, wherein the lubricating oil passage is formed by a cutout portion that is cut out to the outer periphery in the radial direction in the thrust runner. 【請求項３】請求項１において、前記潤滑油路は、前記
スラストランナに、両面に貫通する孔部によって形成さ
れることを特徴とするスラスト軸受装置。3. The thrust bearing device according to claim 1, wherein the lubricating oil passage is formed in the thrust runner by holes penetrating both sides. 【請求項４】請求項１において、潤滑油路の全部または
その一部は摺動接触する面の中心を通る線の内側に形成
されることを特徴とするスラスト軸受装置。4. The thrust bearing device according to claim 1, wherein all or part of the lubricating oil passage is formed inside a line passing through the center of the surface in sliding contact. 【請求項５】請求項１から４のいずれかにおいて、 前記スラストランナの双方の面のいずれかの面には、円
周方向に延びるテーパ部が形成されていることを特徴と
するスラスト軸受装置。5. The thrust bearing device according to claim 1, wherein a taper portion extending in a circumferential direction is formed on one of both surfaces of the thrust runner. . 【請求項６】請求項１から５のいずれかにおいて、 前記スラストランナの他方の面に、固体潤滑材によるコ
ーティング層を設けたことを特徴とするスラスト軸受装
置。6. The thrust bearing device according to claim 1, wherein a coating layer made of a solid lubricant is provided on the other surface of the thrust runner.
JP2001363401A 2001-11-28 2001-11-28 Thrust bearing unit for turbocharger Pending JP2003166537A (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
JP2001363401A JP2003166537A (en) 2001-11-28 2001-11-28 Thrust bearing unit for turbocharger

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
JP2001363401A JP2003166537A (en) 2001-11-28 2001-11-28 Thrust bearing unit for turbocharger

Publications (1)

Publication Number Publication Date
JP2003166537A true JP2003166537A (en) 2003-06-13

Family

ID=19173748

Family Applications (1)

Application Number Title Priority Date Filing Date
JP2001363401A Pending JP2003166537A (en) 2001-11-28 2001-11-28 Thrust bearing unit for turbocharger

Country Status (1)

Country Link
JP (1) JP2003166537A (en)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2013185443A (en) * 2012-03-06 2013-09-19 Taiho Kogyo Co Ltd Bearing device

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2013185443A (en) * 2012-03-06 2013-09-19 Taiho Kogyo Co Ltd Bearing device

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