JP2001295655A - Bearing structure of turbocharger - Google Patents
Bearing structure of turbochargerInfo
- Publication number
- JP2001295655A JP2001295655A JP2000109783A JP2000109783A JP2001295655A JP 2001295655 A JP2001295655 A JP 2001295655A JP 2000109783 A JP2000109783 A JP 2000109783A JP 2000109783 A JP2000109783 A JP 2000109783A JP 2001295655 A JP2001295655 A JP 2001295655A
- Authority
- JP
- Japan
- Prior art keywords
- bearing
- thrust
- rotor shaft
- support surface
- housing
- 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.)
- Granted
Links
- 238000013016 damping Methods 0.000 claims abstract description 13
- 239000000463 material Substances 0.000 claims abstract description 7
- 238000003754 machining Methods 0.000 abstract description 13
- 238000000034 method Methods 0.000 abstract description 4
- 239000002184 metal Substances 0.000 description 10
- 229910052751 metal Inorganic materials 0.000 description 10
- 238000002485 combustion reaction Methods 0.000 description 6
- 238000003780 insertion Methods 0.000 description 6
- 230000037431 insertion Effects 0.000 description 6
- 150000002739 metals Chemical class 0.000 description 6
- 238000010586 diagram Methods 0.000 description 4
- 239000003921 oil Substances 0.000 description 4
- 230000003746 surface roughness Effects 0.000 description 4
- 239000000446 fuel Substances 0.000 description 3
- 239000000203 mixture Substances 0.000 description 3
- 229920006351 engineering plastic Polymers 0.000 description 2
- 238000004519 manufacturing process Methods 0.000 description 2
- 125000006850 spacer group Chemical group 0.000 description 2
- 230000002159 abnormal effect Effects 0.000 description 1
- 230000006835 compression Effects 0.000 description 1
- 238000007906 compression Methods 0.000 description 1
- 230000002950 deficient Effects 0.000 description 1
- 238000006073 displacement reaction Methods 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 239000006260 foam Substances 0.000 description 1
- 238000009413 insulation Methods 0.000 description 1
- 238000002955 isolation Methods 0.000 description 1
- 239000010687 lubricating oil Substances 0.000 description 1
- 238000003466 welding Methods 0.000 description 1
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
- F16C35/00—Rigid support of bearing units; Housings, e.g. caps, covers
- F16C35/02—Rigid support of bearing units; Housings, e.g. caps, covers in the case of sliding-contact bearings
-
- 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
- F16C17/02—Sliding-contact bearings for exclusively rotary movement for radial load only
-
- 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
- F16C17/12—Sliding-contact bearings for exclusively rotary movement characterised by features not related to the direction of the load
- F16C17/18—Sliding-contact bearings for exclusively rotary movement characterised by features not related to the direction of the load with floating brasses or brushing, rotatable at a reduced speed
-
- 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)
- Supercharger (AREA)
- Sliding-Contact Bearings (AREA)
- Mounting Of Bearings Or Others (AREA)
Abstract
(57)【要約】
【課題】 タービンロータ軸及びコンプレッサインペラ
の高速回転を正確な位置で確実に支持でき、かつベアリ
ングハウジングに要求される加工精度を下げて汎用の加
工設備で短時間に高い歩留りで加工することができ、更
にアンバランスにより発生する高周波振動を効果的に減
衰することができる過給機の軸受構造を提供する。
【解決手段】 ロータ軸１ｂの回転を支持する軸受ユニ
ット１２と、軸受ユニットを内側に固定する貫通孔１４
ａを有するベアリングハウジング１４とを備える。軸受
ユニットは、ロータ軸を支持するラジアル軸受を内蔵す
る中空円筒形の軸受スリーブ１３を有し、その端部にス
ラスト支持面１３ａが設けられる。軸受スリーブ１３
は、減衰性を有する減衰材料からなる。またベアリング
ハウジングは、スラスト支持面１３ａに平行なスラスト
軸受取付面１４ｂを有する。スラスト支持面１３ａとス
ラスト軸受取付面１４ｂとが軸方向に所定の間隔を隔て
るように圧入され、止まり嵌めで固定される。
(57) [Summary] [PROBLEMS] To provide high-speed rotation of a turbine rotor shaft and a compressor impeller reliably at an accurate position, reduce machining accuracy required for a bearing housing, and achieve high yield in a short time with general-purpose machining equipment. The present invention provides a bearing structure of a supercharger, which can be processed by the above method, and can effectively attenuate high-frequency vibration generated by imbalance. A bearing unit for supporting rotation of a rotor shaft, and a through hole for fixing the bearing unit inside.
a bearing housing 14 having a. The bearing unit has a hollow cylindrical bearing sleeve 13 containing a radial bearing for supporting the rotor shaft, and a thrust support surface 13a is provided at an end thereof. Bearing sleeve 13
Is made of a damping material having a damping property. The bearing housing has a thrust bearing mounting surface 14b parallel to the thrust support surface 13a. The thrust support surface 13a and the thrust bearing mounting surface 14b are press-fitted at predetermined intervals in the axial direction, and are fixed with a stop fit.
Description
【０００１】[0001]
【発明の属する技術分野】本発明は、過給機の軸受構造
に関する。The present invention relates to a bearing structure for a turbocharger.
【０００２】[0002]
【従来の技術】内燃機関のシリンダに供給される空気或
いは混合気をあらかじめ圧縮することを過給といい、そ
の圧縮機を過給機（ｓｕｐｅｒｃｈａｒｇｅｒ）とい
う。また、そのうち機関の排気ガスを利用したガスター
ビンに直結した過給機を排気タービン過給機、または略
してターボ過給機（ｔｕｒｂｏｃｈａｒｇｅｒ）とい
う。なお、以下の説明において、特に必要な場合を除
き、ターボ過給機を単に「過給機」と呼ぶ。2. Description of the Related Art The pre-compression of air or air-fuel mixture supplied to a cylinder of an internal combustion engine is called supercharging, and the compressor is called a supercharger. In addition, a supercharger directly connected to a gas turbine using exhaust gas of the engine is referred to as an exhaust turbine supercharger, or a turbocharger for short. In the following description, a turbocharger will be simply referred to as a "supercharger" unless otherwise required.
【０００３】図３は、従来のターボ過給機の一例を示す
全体構成図である。この図において、ターボ過給機は、
タービンロータ軸１、コンプレッサインペラ２、ベアリ
ングハウジング３、タービンハウジング４、コンプレッ
サハウジング５ａ、シールプレート５ｂ、等からなる。
ベアリングハウジング３、タービンハウジング４、コン
プレッサハウジング５ａ、及びシールプレート５ｂは図
示の順序で互いに連結されている。また、タービンロー
タ軸１は、タービンインペラ１ａとロータ軸１ｂが溶接
等で一体化されており、ベアリングハウジング３で回転
支持され、コンプレッサインペラ２に同軸に連結されて
いる。この構成により、内燃機関の排気ガスでタービン
インペラ１ａを回転駆動し、その回転力をロータ軸１ｂ
を介してコンプレッサインペラ２に伝達してこれを回転
駆動し、空気（又は混合気）を圧縮して内燃機関に供給
することにより内燃機関の性能を大幅に向上させること
ができる。FIG. 3 is an overall configuration diagram showing an example of a conventional turbocharger. In this figure, the turbocharger is
It comprises a turbine rotor shaft 1, a compressor impeller 2, a bearing housing 3, a turbine housing 4, a compressor housing 5a, a seal plate 5b, and the like.
The bearing housing 3, the turbine housing 4, the compressor housing 5a, and the seal plate 5b are connected to each other in the order shown. The turbine rotor shaft 1 has a turbine impeller 1 a and a rotor shaft 1 b integrated by welding or the like, is rotatably supported by a bearing housing 3, and is coaxially connected to the compressor impeller 2. With this configuration, the turbine impeller 1a is rotationally driven by the exhaust gas of the internal combustion engine, and the rotational force is applied to the rotor shaft 1b.
The compressor (2) is transmitted to the compressor impeller (2), and is rotationally driven to compress and supply the air (or air-fuel mixture) to the internal combustion engine, thereby greatly improving the performance of the internal combustion engine.
【０００４】図３において、タービンインペラ１ａの回
転は、２つのフローティングメタル６ａ，６ｂでラジア
ル方向を支持され、スラストカラー７を介してタービン
側スラストベアリング８ａとコンプレッサ側スラストベ
アリング８ｂでスラスト方向を支持される。なお、この
図で、９は油切り、６ｃは軸受スペーサ、１０は遮熱
板、１１はシールリングである。In FIG. 3, the rotation of the turbine impeller 1a is supported in the radial direction by two floating metals 6a and 6b, and the thrust direction is supported by a turbine-side thrust bearing 8a and a compressor-side thrust bearing 8b via a thrust collar 7. Is done. In this figure, 9 is an oil drain, 6c is a bearing spacer, 10 is a heat shield plate, and 11 is a seal ring.
【０００５】過給機の高性能化に伴い、タービンロータ
軸１及びコンプレッサインペラ２は、数万〜数１０万ｍ
ｉｎ-1の高速で回転する。そのため、フローティングメ
タル６ａ，６ｂ及びスラストカラー７は、固定部分と回
転部分の中間速度で回転しながら、ラジアル力及びスラ
スト力を支持するようになっている。また、その回転時
の摺動抵抗を低減するために、ベアリングハウジング３
に設けられた油路３ａから常に潤滑油が摺動部に供給さ
れるようになっている。[0005] With the improvement of the performance of the turbocharger, the turbine rotor shaft 1 and the compressor impeller 2 have tens of thousands to several hundred thousand meters.
It rotates at a high speed of in -1 . Therefore, the floating metals 6a and 6b and the thrust collar 7 support the radial force and the thrust force while rotating at an intermediate speed between the fixed portion and the rotating portion. In order to reduce the sliding resistance during rotation, the bearing housing 3
The lubricating oil is always supplied to the sliding portion from an oil passage 3a provided in the sliding portion.
【０００６】[0006]
【発明が解決しようとする課題】上述した従来の過給機
において、ベアリングハウジング３の中心部にフローテ
ィングメタル６ａ，６ｂを取り付ける貫通孔Ａを加工
し、かつその貫通孔の端部にタービン側スラストベアリ
ング８ａの受面Ｂを直接加工する必要がある。貫通孔Ａ
は、フローティングメタル６ａ，６ｂを直接支持する摺
動面であるため、高い軸心精度（例えば±２〜３μｍ）
と極めて優れた面粗さ（例えば２〜３μｍ）が要求され
る。また、タービン側スラストベアリング８ａの受面Ｂ
は、スラストカラー７を適切に回転させるために、優れ
た面粗さ（例えば２〜３μｍ）とコンプレッサ側スラス
トベアリング８ｂの取付け面Ｃまでの正確な軸方向間隔
が要求される。そのため、これらの高精度加工のため
に、ベアリングハウジング３の加工には高価な加工設備
を必要とし、加工時間がかかり、かつ不良品の発生率が
高い問題点があった。In the conventional turbocharger described above, a through hole A for mounting the floating metals 6a and 6b is machined at the center of the bearing housing 3, and a turbine-side thrust is formed at an end of the through hole. It is necessary to directly process the receiving surface B of the bearing 8a. Through hole A
Is a sliding surface that directly supports the floating metals 6a and 6b, and therefore has a high axial center accuracy (for example, ± 2 to 3 μm).
And extremely excellent surface roughness (for example, 2 to 3 μm) are required. The receiving surface B of the turbine-side thrust bearing 8a
In order to properly rotate the thrust collar 7, excellent surface roughness (for example, 2 to 3 μm) and an accurate axial distance from the mounting surface C of the compressor-side thrust bearing 8b are required. Therefore, for these high-precision machining, machining of the bearing housing 3 requires expensive machining equipment, and there is a problem that the machining time is long and the occurrence rate of defective products is high.
【０００７】また、前述のようにタービンロータ軸１及
びコンプレッサインペラ２が高速回転するため、わずか
なアンバランスにより過給機が１〜３ｋＨｚの高周波の
振動を起こしやすい。この高周波振動は、剛性の高いベ
アリングハウジング３を介して直接外部に伝達され、異
常音となりやすい問題点があった。Further, as described above, since the turbine rotor shaft 1 and the compressor impeller 2 rotate at a high speed, a slight imbalance tends to cause high-frequency vibration of the turbocharger of 1 to 3 kHz. This high-frequency vibration is directly transmitted to the outside via the highly rigid bearing housing 3, and there is a problem that abnormal sound is likely to occur.
【０００８】本発明は上述した問題点を解決するために
創案されたものである。すなわち、本発明の目的は、タ
ービンロータ軸及びコンプレッサインペラの高速回転を
正確な位置で確実に支持でき、かつベアリングハウジン
グに要求される加工精度を下げて汎用の加工設備で短時
間に高い歩留りで加工することができ、更にアンバラン
スにより発生する高周波振動を効果的に減衰することが
できる過給機の軸受構造を提供することにある。The present invention has been made to solve the above-mentioned problems. That is, an object of the present invention is to reliably support the high-speed rotation of the turbine rotor shaft and the compressor impeller at an accurate position, and reduce the processing accuracy required for the bearing housing to achieve high yield in a short time with general-purpose processing equipment. An object of the present invention is to provide a bearing structure of a turbocharger which can be processed and can effectively attenuate high-frequency vibration generated due to imbalance.
【０００９】[0009]
【課題を解決するための手段】本発明によれば、排気ガ
スでタービンインペラ（１ａ）を回転駆動しロータ軸
（１ｂ）を介してコンプレッサインペラ（２）を回転駆
動する過給機の軸受構造であって、前記ロータ軸の回転
を支持する軸受ユニット（１２）と、該軸受ユニットを
内側に固定する貫通孔（１４ａ）を有するベアリングハ
ウジング（１４）とを備え、該貫通孔（１４ａ）に軸受
ユニット（１２）が圧入され止まり嵌めで固定される、
ことを特徴とする過給機の軸受構造が提供される。According to the present invention, a bearing structure of a supercharger for rotating a turbine impeller (1a) with exhaust gas and rotating a compressor impeller (2) via a rotor shaft (1b) is provided. And a bearing unit (12) for supporting the rotation of the rotor shaft, and a bearing housing (14) having a through hole (14a) for fixing the bearing unit inside, the through hole (14a) being provided in the through hole (14a). The bearing unit (12) is press-fitted and fixed with a stop fit.
A supercharger bearing structure is provided.
【００１０】上記本発明の構成によれば、軸受ユニット
（１２）とベアリングハウジング（１４）の間に多層構
造が形成されため、この間での振動絶縁ができ、低振動
化が図れる。また、軸受ユニット（１２）を貫通孔（１
４ａ）に圧入して止まり嵌めで固定するので、貫通孔
（１４ａ）の内面の面粗さを、止まり嵌めが可能な程度
に粗くできる。従って、ベアリングハウジング側の挿入
部の加工精度を下げて汎用の加工設備で短時間に高い歩
留りで加工することができる。更に、ロータ軸の回転を
支持する軸受部分を軸受ユニット（１２）として独立さ
せたので、このユニットのみをオフラインで製造するこ
とが可能になる。従って、特に精度を有する軸受ユニッ
トのみを別ライン又は別会社で製造・組立することがで
き、過給機組立ライン上での組立工程を削減することが
できる。According to the structure of the present invention, since a multilayer structure is formed between the bearing unit (12) and the bearing housing (14), vibration insulation can be performed between them and low vibration can be achieved. Further, the bearing unit (12) is inserted into the through hole (1).
4a), the surface of the through hole (14a) can be roughened to the extent that the stop fit is possible. Therefore, the machining accuracy of the insertion portion on the bearing housing side can be reduced, and machining can be performed with high yield in a short time with general-purpose machining equipment. Further, since the bearing portion for supporting the rotation of the rotor shaft is made independent as the bearing unit (12), only this unit can be manufactured off-line. Therefore, it is possible to manufacture and assemble only the bearing unit having particularly high accuracy in another line or another company, and it is possible to reduce an assembling process on the supercharger assembling line.
【００１１】本発明の好ましい実施形態によれば、前記
軸受ユニット（１２）は、ロータ軸（１ｂ）を支持する
ラジアル軸受を内蔵する中空円筒形の軸受スリーブ（１
３）を有し、かつその端部にスラスト支持面（１３ａ）
が設けられ、前記ベアリングハウジング（１４）は、前
記スラスト支持面（１３ａ）に平行なスラスト軸受取付
面（１４ｂ）を有し、スラスト支持面（１３ａ）とスラ
スト軸受取付面（１４ｂ）とが軸方向に所定の間隔を隔
てるように圧入される。According to a preferred embodiment of the present invention, the bearing unit (12) has a hollow cylindrical bearing sleeve (1) containing a radial bearing for supporting the rotor shaft (1b).
3) and at its end a thrust support surface (13a)
The bearing housing (14) has a thrust bearing mounting surface (14b) parallel to the thrust support surface (13a), and the thrust support surface (13a) and the thrust bearing mounting surface (14b) are axially connected. It is press-fitted at a predetermined interval in the direction.
【００１２】この構成により、ベアリングハウジング
（１４）の挿入部の加工を貫通孔（１４ａ）と単一のス
ラスト軸受取付面（１４ｂ）のみにでき、挿入部の加工
を更に容易にすることができる。With this configuration, the processing of the insertion portion of the bearing housing (14) can be performed only with the through hole (14a) and the single thrust bearing mounting surface (14b), and the processing of the insertion portion can be further facilitated. .
【００１３】また、前記軸受スリーブ（１３）は、減衰
性を有する減衰材料からなるのが好ましい。この構成に
より、軸受スリーブ（１３）に減衰性を有する減衰材料
（例えば、可撓性のある発泡金属又はエンジニアリング
プラスチック）を用いることにより、アンバランスによ
り発生する高周波振動を効果的に減衰させることができ
る。The bearing sleeve (13) is preferably made of a damping material having damping properties. With this configuration, by using a damping material having damping properties (for example, a flexible foamed metal or engineering plastic) for the bearing sleeve (13), high-frequency vibration generated due to imbalance can be effectively damped. it can.
【００１４】[0014]
【発明の実施の形態】以下、本発明の好ましい実施形態
を図面を参照して説明する。なお、各図において共通部
分には同一の符号を付し、重複した説明を省略する。図
１は、本発明の軸受構造を備えた過給機の全体構成図で
ある。この図において、この過給機は、図３と同一のタ
ーボ過給機であり、内燃機関の排気ガスでタービンイン
ペラ１ａを回転駆動し、その回転力をロータ軸１ｂを介
してコンプレッサインペラ２に伝達してこれを回転駆動
し、空気（又は混合気）を圧縮して内燃機関に供給する
ようになっている。DESCRIPTION OF THE PREFERRED EMBODIMENTS Preferred embodiments of the present invention will be described below with reference to the drawings. In the drawings, common parts are denoted by the same reference numerals, and redundant description is omitted. FIG. 1 is an overall configuration diagram of a supercharger provided with the bearing structure of the present invention. In this figure, this supercharger is the same turbocharger as that of FIG. 3, and drives the turbine impeller 1 a to rotate by the exhaust gas of the internal combustion engine, and transmits the rotational force to the compressor impeller 2 via the rotor shaft 1 b. The air is transmitted and driven to rotate, compressing the air (or air-fuel mixture) and supplying it to the internal combustion engine.
【００１５】また、本発明の軸受構造では、ロータ軸１
ｂの回転を支持する軸受ユニット１２と、軸受ユニット
を内側に固定する貫通孔１４ａを有するベアリングハウ
ジング１４とを備える。更に、この図において軸受ユニ
ット１２は、ベアリングハウジング１４の貫通孔１４ａ
に圧入され止まり嵌めで固定されている。In the bearing structure of the present invention, the rotor shaft 1
The bearing unit 12 includes a bearing unit 12 that supports the rotation of the bearing unit b, and a bearing housing 14 having a through hole 14a that fixes the bearing unit inside. Further, in this figure, the bearing unit 12 is provided with a through hole 14a of the bearing housing 14.
And is fixed with a stop fit.
【００１６】図２は、図１の主要部の部分分解図であ
る。この図に示すように、軸受ユニット１２は、中空円
筒形の軸受スリーブ１３と、軸受スリーブ１３の内部に
組み込まれたラジアル軸受からなる。ラジアル軸受は、
この例では、フローティングメタル６ａ，６ｂである。FIG. 2 is a partially exploded view of the main part of FIG. As shown in this figure, the bearing unit 12 includes a hollow cylindrical bearing sleeve 13 and a radial bearing incorporated inside the bearing sleeve 13. Radial bearings
In this example, they are the floating metals 6a and 6b.
【００１７】ベアリングハウジング１４の貫通孔１４ａ
と軸受スリーブ１３の外径は、軸受ユニット１２を貫通
孔１４ａに圧入し止まり嵌めで位置決めできる限りで、
比較的粗い面に仕上げられている。この「止まり嵌め」
の公差は、過給機の運転時に作用するスラスト力により
位置ズレが生じない程度に大きく設定する。一方、フロ
ーティングメタル６ａ，６ｂと接触する軸受スリーブ１
３の支持面は、従来と同様に高い軸心精度（例えば±２
〜３μｍ）と極めて優れた面粗さ（例えばＲａ２〜３μ
ｍ）で製作する。この加工は、軸受スリーブ１３を単独
で加工するため、汎用の加工設備（例えば汎用の旋盤
等）で短時間に効率よく加工することができる。The through hole 14a of the bearing housing 14
And the outer diameter of the bearing sleeve 13 as long as the bearing unit 12 can be press-fitted into the through hole 14a and positioned by a stop fit.
Finished on a relatively rough surface. This "stop fit"
Is set to be large enough to prevent the displacement from occurring due to the thrust force acting during the operation of the turbocharger. On the other hand, the bearing sleeve 1 in contact with the floating metals 6a and 6b
3 has a high axial accuracy (for example, ± 2
~ 3 µm) and extremely excellent surface roughness (for example, Ra2 ~ 3 µm).
m). In this processing, since the bearing sleeve 13 is processed alone, the processing can be efficiently performed in a short time using general-purpose processing equipment (for example, a general-purpose lathe).
【００１８】また、図２に示すように、軸受スリーブ１
３の端部には、スラスト支持面１３ａが設けられ、ベア
リングハウジング１４には、スラスト支持面１３ａに平
行なスラスト軸受取付面１４ｂが設けられる。スラスト
支持面１３ａとスラスト軸受取付面１４ｂはそれぞれ軸
線に垂直な平面であり、かつそれぞれ独立に加工する。
また、軸受スリーブ１３は、減衰性を有する減衰材料、
例えば可撓性のある発泡金属、エンジニアリングプラス
チック、或いはその他の減衰材料から製造するのがよ
い。Further, as shown in FIG.
A thrust support surface 13a is provided at an end of the shaft 3, and a thrust bearing mounting surface 14b parallel to the thrust support surface 13a is provided in the bearing housing 14. The thrust support surface 13a and the thrust bearing mounting surface 14b are planes perpendicular to the axis, respectively, and are processed independently.
The bearing sleeve 13 is made of a damping material having damping properties,
For example, it may be manufactured from a flexible foam metal, engineering plastic, or other damping material.
【００１９】上述のように加工・製造したベアリングハ
ウジング１４に、予めフローティングメタル６ａ，６ｂ
を組み込んだ軸受ユニット１２を図２に矢印で示すよう
に、同軸に圧入し、スラスト支持面１３ａとスラスト軸
受取付面１４ｂとが軸方向に所定の間隔を隔てるように
位置決めする。その後、タービン側スラストベアリング
８ａ、スラストカラー７、コンプレッサ側スラストベア
リング８ｂ等を軸方向に組み付けることにより、図１に
示す過給機を組み立てることができる。The floating metal 6a, 6b is previously placed on the bearing housing 14 machined and manufactured as described above.
2 is coaxially press-fitted as indicated by an arrow in FIG. 2 and positioned so that the thrust support surface 13a and the thrust bearing mounting surface 14b are spaced apart from each other in the axial direction by a predetermined distance. Thereafter, the turbocharger shown in FIG. 1 can be assembled by assembling the turbine-side thrust bearing 8a, the thrust collar 7, the compressor-side thrust bearing 8b, and the like in the axial direction.
【００２０】上述した本発明の構成によれば、軸受ユニ
ット１２とベアリングハウジング１４の間に多層構造が
形成されため、この間での振動絶縁ができ、低振動化が
図れる。更に軸受スリーブ１３に減衰性を有する減衰材
料を用いることにより、アンバランスにより発生する高
周波振動を効果的に減衰させることができる。According to the above-described structure of the present invention, since a multilayer structure is formed between the bearing unit 12 and the bearing housing 14, vibration isolation between the bearing unit 12 and the bearing housing 14 can be achieved, and low vibration can be achieved. Further, by using a damping material having a damping property for the bearing sleeve 13, high-frequency vibration generated due to imbalance can be effectively damped.
【００２１】また、軸受ユニット１２を貫通孔１４ａに
圧入して止まり嵌めで固定するので、貫通孔１４ａの内
面の面粗さを、止まり嵌めが可能な程度に粗くできる。
更に、ベアリングハウジング１４の挿入部の加工を貫通
孔１４ａと単一のスラスト軸受取付面１４ｂのみにで
き、挿入部の加工を更に容易にすることができる。従っ
て、ベアリングハウジング側の挿入部の加工精度を下げ
て汎用の加工設備で短時間に高い歩留りで加工すること
ができる。Further, since the bearing unit 12 is press-fitted into the through-hole 14a and fixed by the stop fit, the surface roughness of the inner surface of the through-hole 14a can be made rough enough to allow the stop fit.
Further, the processing of the insertion portion of the bearing housing 14 can be performed only with the through hole 14a and the single thrust bearing mounting surface 14b, and the processing of the insertion portion can be further facilitated. Therefore, the machining accuracy of the insertion portion on the bearing housing side can be reduced, and machining can be performed with high yield in a short time with general-purpose machining equipment.
【００２２】更に、ロータ軸の回転を支持する軸受部分
を軸受ユニット１２として独立させたので、このユニッ
トのみをオフラインで製造することが可能になる。従っ
て、特に精度を有する軸受ユニットのみを別ライン又は
別会社で製造・組立することができ、過給機組立ライン
上での組立工程を削減することができる。Further, since the bearing portion for supporting the rotation of the rotor shaft is made independent as the bearing unit 12, only this unit can be manufactured off-line. Therefore, it is possible to manufacture and assemble only the bearing unit having particularly high accuracy in another line or another company, and it is possible to reduce an assembling process on the supercharger assembling line.
【００２３】なお、本発明は上述した実施の形態に限定
されず、本発明の要旨を逸脱しない範囲で種々変更でき
ることは勿論である。It should be noted that the present invention is not limited to the above-described embodiment, and it goes without saying that various changes can be made without departing from the spirit of the present invention.
【００２４】[0024]
【発明の効果】上述したように、本発明の過給機の軸受
構造は、タービンロータ軸及びコンプレッサインペラの
高速回転を正確な位置で確実に支持でき、かつベアリン
グハウジングに要求される加工精度を下げて汎用の加工
設備で短時間に高い歩留りで加工することができ、更に
アンバランスにより発生する高周波振動を効果的に減衰
することができる、等の優れた効果を有する。As described above, the bearing structure of the turbocharger of the present invention can reliably support the high-speed rotation of the turbine rotor shaft and the compressor impeller at an accurate position, and can reduce the machining accuracy required for the bearing housing. It has excellent effects such as being able to perform processing at a high yield in a short time with general-purpose processing equipment by lowering, and to be able to effectively attenuate high-frequency vibration generated due to imbalance.
【図１】本発明の軸受構造を備えた過給機の全体構成図
である。FIG. 1 is an overall configuration diagram of a supercharger provided with a bearing structure of the present invention.
【図２】図１の主要部の部分分解図である。FIG. 2 is a partially exploded view of a main part of FIG.
【図３】従来のターボ過給機の一例を示す全体構成図で
ある。FIG. 3 is an overall configuration diagram showing an example of a conventional turbocharger.
１ タービンロータ軸、１ａ タービンインペラ、１ｂ
ロータ軸、２ コンプレッサインペラ、３ ベアリン
グハウジング、３ａ 油路、４ タービンハウジング、
５ａ コンプレッサハウジング、５ｂ シールプレー
ト、６ａ，６ｂ フローティングメタル、６ｃ 軸受ス
ペーサ、７ スラストカラー、８ａ タービン側スラス
トベアリング、８ｂ コンプレッサ側スラストベアリン
グ、９ 油切り、１０ 遮熱板、１１ シールリング、
１２ 軸受ユニット、１３ 軸受スリーブ、１３ａ ス
ラスト支持面、１４ ベアリングハウジング、１４ａ
貫通孔、１４ｂ スラスト軸受取付面1 Turbine rotor shaft, 1a Turbine impeller, 1b
Rotor shaft, 2 compressor impeller, 3 bearing housing, 3a oil passage, 4 turbine housing,
5a compressor housing, 5b seal plate, 6a, 6b floating metal, 6c bearing spacer, 7 thrust collar, 8a turbine-side thrust bearing, 8b compressor-side thrust bearing, 9 oil drain, 10 heat shield plate, 11 seal ring,
12 bearing unit, 13 bearing sleeve, 13a thrust support surface, 14 bearing housing, 14a
Through hole, 14b thrust bearing mounting surface
───────────────────────────────────────────────────── フロントページの続き Ｆターム(参考） 3G005 EA04 EA16 FA41 GB55 GB59 KA00 3J011 AA01 BA02 BA08 3J017 AA03 BA01 CA01 DB07 ──────────────────────────────────────────────────続 き Continued on the front page F term (reference) 3G005 EA04 EA16 FA41 GB55 GB59 KA00 3J011 AA01 BA02 BA08 3J017 AA03 BA01 CA01 DB07
Claims (3)
回転駆動しロータ軸（１ｂ）を介してコンプレッサイン
ペラ（２）を回転駆動する過給機の軸受構造であって、 前記ロータ軸の回転を支持する軸受ユニット（１２）
と、 該軸受ユニットを内側に固定する貫通孔（１４ａ）を有
するベアリングハウジング（１４）とを備え、該貫通孔
（１４ａ）に軸受ユニット（１２）が圧入され止まり嵌
めで固定される、ことを特徴とする過給機の軸受構造。1. A bearing structure of a supercharger for rotating a turbine impeller (1a) with exhaust gas and rotating a compressor impeller (2) via a rotor shaft (1b), wherein the rotation of the rotor shaft is controlled. Bearing unit to support (12)
And a bearing housing (14) having a through-hole (14a) for fixing the bearing unit inside, wherein the bearing unit (12) is press-fitted into the through-hole (14a) and fixed by a stop fit. Characteristic turbocharger bearing structure.
（１ｂ）を支持するラジアル軸受を内蔵する中空円筒形
の軸受スリーブ（１３）を有し、かつその端部にスラス
ト支持面（１３ａ）が設けられ、 前記ベアリングハウジング（１４）は、前記スラスト支
持面（１３ａ）に平行なスラスト軸受取付面（１４ｂ）
を有し、 スラスト支持面（１３ａ）とスラスト軸受取付面（１４
ｂ）とが軸方向に所定の間隔を隔てるように圧入され
る、ことを特徴とする請求項１に記載の過給機の軸受構
造。2. The bearing unit (12) has a hollow cylindrical bearing sleeve (13) containing a radial bearing for supporting a rotor shaft (1b), and a thrust support surface (13a) at an end thereof. The bearing housing (14) is provided with a thrust bearing mounting surface (14b) parallel to the thrust support surface (13a).
And a thrust support surface (13a) and a thrust bearing mounting surface (14).
2. The bearing structure for a turbocharger according to claim 1, wherein b) and b) are press-fitted at predetermined intervals in the axial direction.
有する減衰材料からなる、ことを特徴とする請求項２に
記載の過給機の軸受構造。3. The bearing structure of a turbocharger according to claim 2, wherein the bearing sleeve (13) is made of a damping material having a damping property.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2000109783A JP4407780B2 (en) | 2000-04-11 | 2000-04-11 | Turbocharger bearing structure |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2000109783A JP4407780B2 (en) | 2000-04-11 | 2000-04-11 | Turbocharger bearing structure |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JP2001295655A true JP2001295655A (en) | 2001-10-26 |
| JP4407780B2 JP4407780B2 (en) | 2010-02-03 |
Family
ID=18622414
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP2000109783A Expired - Fee Related JP4407780B2 (en) | 2000-04-11 | 2000-04-11 | Turbocharger bearing structure |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JP4407780B2 (en) |
Cited By (14)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2007108234A1 (en) | 2006-03-23 | 2007-09-27 | Ihi Corporation | High-speed rotating shaft for supercharger |
| US7673452B2 (en) | 2006-01-24 | 2010-03-09 | Ishikawajima-Harima Heavy Industries Co., Ltd. | Motor-driven supercharger |
| US7837448B2 (en) | 2006-01-26 | 2010-11-23 | Ishikawajima-Harima Heavy Industries Co., Ltd. | Supercharger |
| US8001781B2 (en) | 2006-06-02 | 2011-08-23 | Ihi Corporation | Motor-driven supercharger |
| CN102369357A (en) * | 2009-04-07 | 2012-03-07 | 戴姆勒股份公司 | Sleeve element for axially fixing a bearing in a turbocharger |
| US8157544B2 (en) | 2006-08-18 | 2012-04-17 | Ihi Corporation | Motor driven supercharger with motor/generator cooling efficacy |
| WO2012027188A3 (en) * | 2010-08-24 | 2012-04-26 | Borgwarner Inc. | Bearing housing of an exhaust-gas turbocharger |
| JP2012527576A (en) * | 2009-05-19 | 2012-11-08 | ボーグワーナー インコーポレーテッド | Turbocharger |
| KR20140030673A (en) * | 2012-09-03 | 2014-03-12 | 한라비스테온공조 주식회사 | An air blower for fuel cell vehicle |
| KR20140103296A (en) * | 2011-12-09 | 2014-08-26 | 보르그워너 인코퍼레이티드 | Bearing housing of an exhaust-gas turbocharger |
| WO2016027617A1 (en) * | 2014-08-21 | 2016-02-25 | 株式会社Ihi | Bearing structure and supercharger |
| WO2017020995A1 (en) * | 2015-08-04 | 2017-02-09 | Ihi Charging Systems International Gmbh | Bearing device for an exhaust gas turbocharger having two radial sliding bearings connected by a spacer, and exhaust gas turbocharger having such a bearing device |
| JP2018040286A (en) * | 2016-09-07 | 2018-03-15 | いすゞ自動車株式会社 | Bearing device |
| EP3511577B1 (en) * | 2011-05-04 | 2023-04-12 | Garrett Transportation I Inc. | Bearing assembly with damping features |
Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN108350932B (en) * | 2015-11-13 | 2020-01-21 | 株式会社Ihi | Bearing structure and supercharger |
-
2000
- 2000-04-11 JP JP2000109783A patent/JP4407780B2/en not_active Expired - Fee Related
Cited By (25)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US7673452B2 (en) | 2006-01-24 | 2010-03-09 | Ishikawajima-Harima Heavy Industries Co., Ltd. | Motor-driven supercharger |
| US7837448B2 (en) | 2006-01-26 | 2010-11-23 | Ishikawajima-Harima Heavy Industries Co., Ltd. | Supercharger |
| US8157543B2 (en) | 2006-03-23 | 2012-04-17 | Ihi Corporation | High-speed rotating shaft of supercharger |
| WO2007108234A1 (en) | 2006-03-23 | 2007-09-27 | Ihi Corporation | High-speed rotating shaft for supercharger |
| US8001781B2 (en) | 2006-06-02 | 2011-08-23 | Ihi Corporation | Motor-driven supercharger |
| US8157544B2 (en) | 2006-08-18 | 2012-04-17 | Ihi Corporation | Motor driven supercharger with motor/generator cooling efficacy |
| US9091276B2 (en) | 2009-04-07 | 2015-07-28 | Daimler Ag | Sleeve element for axially fixing a bearing and exhaust gas turbocharger |
| JP2012522935A (en) * | 2009-04-07 | 2012-09-27 | ダイムラー・アクチェンゲゼルシャフト | Sleeve element and exhaust turbocharger for axial fixing |
| CN102369357A (en) * | 2009-04-07 | 2012-03-07 | 戴姆勒股份公司 | Sleeve element for axially fixing a bearing in a turbocharger |
| CN102369357B (en) * | 2009-04-07 | 2014-11-05 | 戴姆勒股份公司 | Sleeve element for axially fixing a bearing in a turbocharger |
| JP2012527576A (en) * | 2009-05-19 | 2012-11-08 | ボーグワーナー インコーポレーテッド | Turbocharger |
| WO2012027188A3 (en) * | 2010-08-24 | 2012-04-26 | Borgwarner Inc. | Bearing housing of an exhaust-gas turbocharger |
| CN103038480A (en) * | 2010-08-24 | 2013-04-10 | 博格华纳公司 | Bearing housing of an exhaust-gas turbocharger |
| CN103038480B (en) * | 2010-08-24 | 2015-10-21 | 博格华纳公司 | Bearing housing for exhaust turbocharger |
| EP3511577B1 (en) * | 2011-05-04 | 2023-04-12 | Garrett Transportation I Inc. | Bearing assembly with damping features |
| KR20140103296A (en) * | 2011-12-09 | 2014-08-26 | 보르그워너 인코퍼레이티드 | Bearing housing of an exhaust-gas turbocharger |
| JP2015500428A (en) * | 2011-12-09 | 2015-01-05 | ボーグワーナー インコーポレーテッド | Exhaust gas turbocharger bearing housing |
| KR101979808B1 (en) * | 2011-12-09 | 2019-08-28 | 보르그워너 인코퍼레이티드 | Bearing housing of an exhaust-gas turbocharger |
| KR101905913B1 (en) * | 2012-09-03 | 2018-10-10 | 현대자동차주식회사 | An air blower for fuel cell vehicle |
| KR20140030673A (en) * | 2012-09-03 | 2014-03-12 | 한라비스테온공조 주식회사 | An air blower for fuel cell vehicle |
| WO2016027617A1 (en) * | 2014-08-21 | 2016-02-25 | 株式会社Ihi | Bearing structure and supercharger |
| CN106460652A (en) * | 2014-08-21 | 2017-02-22 | 株式会社Ihi | Bearing structure and supercharger |
| JPWO2016027617A1 (en) * | 2014-08-21 | 2017-04-27 | 株式会社Ihi | Bearing structure and turbocharger |
| WO2017020995A1 (en) * | 2015-08-04 | 2017-02-09 | Ihi Charging Systems International Gmbh | Bearing device for an exhaust gas turbocharger having two radial sliding bearings connected by a spacer, and exhaust gas turbocharger having such a bearing device |
| JP2018040286A (en) * | 2016-09-07 | 2018-03-15 | いすゞ自動車株式会社 | Bearing device |
Also Published As
| Publication number | Publication date |
|---|---|
| JP4407780B2 (en) | 2010-02-03 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| JP2001295655A (en) | Bearing structure of turbocharger | |
| JPH0540273Y2 (en) | ||
| US11008868B2 (en) | Balancing method for a turbocharger | |
| US7878758B2 (en) | Turbocharger with balancing features | |
| CN102071979B (en) | For the positioning means of turbo-charger bearing | |
| US5964663A (en) | Double diaphragm compound shaft | |
| US7470115B2 (en) | Outer diameter nut piloting for improved rotor balance | |
| US10392970B2 (en) | Rotor shaft architectures for a gas turbine engine and methods of assembly thereof | |
| CA2626978A1 (en) | Support dampers for bearing assemblies and methods of manufacture | |
| JP2011153668A (en) | Bearing device | |
| CN109790847A (en) | Modularization turbocompressor shaft | |
| JP2016191465A (en) | Bearing device and exhaust gas turbocharger | |
| EP3712391B1 (en) | Strut dampening assembly and method of making same | |
| EP3628823A1 (en) | Seal arrangement | |
| EP4609974A1 (en) | Cutting tool support for in-situ hole manufacturing | |
| JP2001115858A (en) | Method for connecting air duct of gas turbine engine and assembly | |
| JP2002138846A (en) | Turbocharger bearing device | |
| EP4130438A1 (en) | Damping bracket for a gas turbine engine | |
| US11754115B1 (en) | Multi-material bushing for rotatably mounting a rotating structure to a stationary structure | |
| CN114382550B (en) | Damping device for damping shaft vibrations | |
| CN211343142U (en) | Gas turbine centering structure, rotor system and generator set | |
| US11852031B2 (en) | Conduit bracket for a gas turbine engine | |
| JP2002039182A (en) | Noncontact bearing spindle device | |
| JP2008291810A (en) | Turbocharger | |
| US9746033B2 (en) | Eccentrically bored sleeve for locating a bearing |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| A621 | Written request for application examination |
Free format text: JAPANESE INTERMEDIATE CODE: A621 Effective date: 20070307 |
|
| A977 | Report on retrieval |
Free format text: JAPANESE INTERMEDIATE CODE: A971007 Effective date: 20090626 |
|
| A131 | Notification of reasons for refusal |
Free format text: JAPANESE INTERMEDIATE CODE: A131 Effective date: 20090730 |
|
| A521 | Written amendment |
Free format text: JAPANESE INTERMEDIATE CODE: A523 Effective date: 20090928 |
|
| TRDD | Decision of grant or rejection written | ||
| A01 | Written decision to grant a patent or to grant a registration (utility model) |
Free format text: JAPANESE INTERMEDIATE CODE: A01 Effective date: 20091021 |
|
| A01 | Written decision to grant a patent or to grant a registration (utility model) |
Free format text: JAPANESE INTERMEDIATE CODE: A01 |
|
| A61 | First payment of annual fees (during grant procedure) |
Free format text: JAPANESE INTERMEDIATE CODE: A61 Effective date: 20091103 |
|
| FPAY | Renewal fee payment (event date is renewal date of database) |
Free format text: PAYMENT UNTIL: 20121120 Year of fee payment: 3 |
|
| FPAY | Renewal fee payment (event date is renewal date of database) |
Free format text: PAYMENT UNTIL: 20131120 Year of fee payment: 4 |
|
| LAPS | Cancellation because of no payment of annual fees |