JP2006145034A - Bearing sealing device - Google Patents

Bearing sealing device Download PDF

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Publication number
JP2006145034A
JP2006145034A JP2005329970A JP2005329970A JP2006145034A JP 2006145034 A JP2006145034 A JP 2006145034A JP 2005329970 A JP2005329970 A JP 2005329970A JP 2005329970 A JP2005329970 A JP 2005329970A JP 2006145034 A JP2006145034 A JP 2006145034A
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Japan
Prior art keywords
housing
oil discharge
seal
rotor shaft
sealing device
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Pending
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JP2005329970A
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Japanese (ja)
Inventor
Klaus Naegler
ネグラー クラウス
Ferdinand Werdecker
ヴェルデッカー フェルディナント
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MAN B&W Diesel GmbH
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MAN B&W Diesel GmbH
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Publication of JP2006145034A publication Critical patent/JP2006145034A/en
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/08—Sealings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
    • F01D25/00—Component parts, details, or accessories, not provided for in, or of interest apart from, other groups
    • F01D25/18—Lubricating arrangements
    • F01D25/183—Sealing means
    • F01D25/186—Sealing means for sliding contact 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
    • F16C33/72—Sealings
    • F16C33/76—Sealings of ball or roller bearings
    • F16C33/80—Labyrinth sealings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02C—GAS-TURBINE PLANTS; AIR INTAKES FOR JET-PROPULSION PLANTS; CONTROLLING FUEL SUPPLY IN AIR-BREATHING JET-PROPULSION PLANTS
    • F02C6/00—Plural gas-turbine plants; Combinations of gas-turbine plants with other apparatus; Adaptations of gas-turbine plants for special use
    • F02C6/04—Gas-turbine plants providing heated or pressurised working fluid for other apparatus, e.g. without mechanical power output
    • F02C6/10—Gas-turbine plants providing heated or pressurised working fluid for other apparatus, e.g. without mechanical power output supplying working fluid to a user, e.g. a chemical process, which returns working fluid to a turbine of the plant
    • F02C6/12—Turbochargers, i.e. plants for augmenting mechanical power output of internal-combustion piston engines by increase of charge pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/08—Sealings
    • F04D29/10—Shaft sealings
    • 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
    • F16C33/72—Sealings
    • F16C33/74—Sealings 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
    • F16J—PISTONS; CYLINDERS; SEALINGS
    • F16J15/00—Sealings
    • F16J15/16—Sealings between relatively-moving surfaces
    • F16J15/164—Sealings between relatively-moving surfaces the sealing action depending on movements; pressure difference, temperature or presence of leaking fluid
    • 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
    • F16J—PISTONS; CYLINDERS; SEALINGS
    • F16J15/00—Sealings
    • F16J15/16—Sealings between relatively-moving surfaces
    • F16J15/32—Sealings between relatively-moving surfaces with elastic sealings, e.g. O-rings
    • 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
    • F16J—PISTONS; CYLINDERS; SEALINGS
    • F16J15/00—Sealings
    • F16J15/44—Free-space packings
    • 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
    • F16J—PISTONS; CYLINDERS; SEALINGS
    • F16J15/00—Sealings
    • F16J15/44—Free-space packings
    • F16J15/447—Labyrinth packings
    • F16J15/4472—Labyrinth packings with axial path
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
    • F05D2220/00—Application
    • F05D2220/40—Application in 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
    • F16C2360/00—Engines or pumps
    • F16C2360/23—Gas turbine engines
    • F16C2360/24—Turbochargers

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Chemical & Material Sciences (AREA)
  • Chemical Kinetics & Catalysis (AREA)
  • General Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Supercharger (AREA)
  • Sealing Using Fluids, Sealing Without Contact, And Removal Of Oil (AREA)
  • Sealing Devices (AREA)
  • Sealing Of Bearings (AREA)

Abstract

<P>PROBLEM TO BE SOLVED: To provide a bearing sealing device for a rotor shaft to be lubricated during stop, having improved sealing performance for sealing a bearing housing of an exhaust driven supercharger against introduced lubricant in the axial direction. <P>SOLUTION: A first seal 11 such as a gap, a labyrinth or a piston ring and a second seal 12 such as a small gap 33 or a labyrinth are provided on the rotor shaft 1. Between the first and second seals 11, 12, oil discharge passages 13, 14 extending to the periphery of the rotor shaft 1 is formed to be closed up. The discharge passages 13, 14 are formed by a housing side oil discharge groove 13 and a shaft side oil discharge groove 14 arranged at the coaxial position. At the radially free end of the rotor shaft 1 in the oil discharge passage 13, 14, an annular seal tongue piece 15 is provided protruding into the annular oil discharge passages 13, 14. The tongue piece 15 serves as a barrier which operates on the lubricant entering into the oil discharge passages in the axial direction. <P>COPYRIGHT: (C)2006,JPO&NCIPI

Description

本発明は、導入された潤滑材に対し軸受ハウジングを軸方向に密封する、特に停止中潤滑されるロータ軸の軸受の密封装置に関する。この装置は、特にロータ軸がタービンハウジング内においてハウジング孔を経て案内される片側端でタービンランナを支持し、圧縮機ハウジング内のハウジング孔を経て案内される反対側端で圧縮機インペラを支持する排気駆動式過給機において、ローラ軸のタービンハウジング側軸受装置および／又は圧縮機ハウジング側軸受装置の内部で利用され、タービンハウジングと圧縮機ハウジングの間の中央軸受ハウジングから出て、タービンハウジング側軸受装置および／又は圧縮機ハウジング側軸受装置に導かれる潤滑材に対し、タービンハウジングおよび／又は圧縮機ハウジングを密封する。   The present invention relates to a sealing device for a bearing of a rotor shaft which seals the bearing housing in the axial direction against introduced lubricant, in particular lubricated during a stop. The device supports the turbine runner at one end, in particular the rotor shaft guided in the turbine housing through the housing hole, and the compressor impeller at the opposite end guided through the housing hole in the compressor housing. In the exhaust drive type supercharger, the roller shaft is utilized inside the turbine housing side bearing device and / or the compressor housing side bearing device, and comes out of the central bearing housing between the turbine housing and the compressor housing, and is on the turbine housing side The turbine housing and / or the compressor housing is sealed against lubricant guided to the bearing device and / or the compressor housing side bearing device.

この形式の密封装置、即ち軸封装置は既に古くから知られている。例えば、殊にタービンハウジングからの排気ガスが、不可避の漏れ個所から軸受隙間、即ち軸受ハウジングや軸受体と軸との間の狭い隙間を経て軸受ハウジング内に流入しおよび／又は高速回転時および吸い込まれた空気の高い給気圧時、或いはガソリンエンジンにおいて、圧縮機ハウジングからの燃科ガス・空気混合気が、圧縮機側密封装置を経て軸受ハウジング内に流入するのを防止せねばならない。また、公知のように、低い給気圧での高速回転時に、各軸受ハウジングからの油含有空気・排気ガス混合気が、タービンハウジングおよび／又は圧縮機ハウジングの方向に流れ、内燃機関に流入することも防止せねばならない。   This type of sealing device, i.e. a shaft sealing device, has been known for a long time. For example, in particular, exhaust gas from the turbine housing flows into the bearing housing from an inevitable leak point through a bearing gap, i.e. a narrow gap between the bearing housing or the bearing body and the shaft, and / or during high speed rotation and suction. In the case of a high supply pressure of the generated air or in a gasoline engine, the fuel gas / air mixture from the compressor housing must be prevented from flowing into the bearing housing through the compressor-side sealing device. Further, as is well known, during high-speed rotation at a low supply air pressure, the oil-containing air / exhaust gas mixture from each bearing housing flows toward the turbine housing and / or the compressor housing and flows into the internal combustion engine. Must also be prevented.

該密封装置はラビリンスパッキン又は密封用のピストンリングである。即ち、例えば特許文献１に、排気駆動式過給機の軸封装置ハウジングにおける軸封装置が記載され、該ハウジングは、高圧用タービンハウジング部分と低圧用タービンハウジング部分との間に配置され、作動媒体漏れ流（流体）が軸方向に貫流する。   The sealing device is a labyrinth packing or a sealing piston ring. That is, for example, Patent Document 1 describes a shaft seal device in a shaft seal device housing of an exhaust drive supercharger, which is disposed between a high-pressure turbine housing portion and a low-pressure turbine housing portion and operates. A medium leakage flow (fluid) flows in the axial direction.

軸封装置は、流体の流れ方向に連続して配置され、流体を繰り返して転向させる絞りを備えたラビリンスを形成している。ラビリンスは、公知の如く軸受ハウジングや軸受体に設けられ、例えばロータ軸の溝にはめ込まれたピストンリングによっても実現できる。   The shaft seal device is arranged continuously in the fluid flow direction, and forms a labyrinth having a throttle that repeatedly turns the fluid. The labyrinth is provided in a bearing housing or a bearing body as is well known, and can be realized by a piston ring fitted in a groove of the rotor shaft, for example.

従来のこの種密封装置は、追加潤滑過程中や予備潤滑過程中に、タービン流れ室および圧縮機流れ室における吸込み（負圧）と関連して、潤滑油を中央軸受ハウジングから吸い出す欠点がある。これは、排気駆動式過給機の全損に至る迄の重大な損傷を生じさせる。
独国特許第２５１３５８２号明細書 This type of conventional sealing device has the disadvantage that the lubricating oil is sucked out of the central bearing housing in connection with the suction (negative pressure) in the turbine flow chamber and the compressor flow chamber during the additional lubrication process and the pre-lubrication process. This causes serious damage up to the total loss of the exhaust-driven turbocharger.
German Patent No. 2513582

本発明の課題は、特に上述の如きロータ軸付き排気駆動式過給機に利用される冒頭に述べた形式の密封装置の密封性を、特にロータ軸の停止状態において改善することにある。   The object of the present invention is to improve the sealing performance of the sealing device of the type mentioned at the beginning, in particular used in an exhaust-drive supercharger with a rotor shaft as described above, in particular when the rotor shaft is stopped.

本発明に基づき、この課題は、密封装置を形成すべくロータ軸に、隙間、ラビリンス又はピストンリングの形態の第１シールと、狭い隙間やラビリンスの形態の第２シールが設けられ、この第１、第２シール間に、ロータ軸の周りを延びる油排出路が封じ込まれ、該油排出路が、ハウジング側油排出溝と、同軸位置に配置された軸側油排出溝とで構成され、この排出路内に、ロータ軸の半径方向に自由端が環状油排出路内に突出する環状シール舌片が設けられ、該シール舌片が油排出路に侵入する潤滑材に対し軸方向に作用するバリアを形成することで解決される。   In accordance with the present invention, the object is to provide the rotor shaft with a first seal in the form of a gap, labyrinth or piston ring and a second seal in the form of a narrow gap or labyrinth to form a sealing device. The oil discharge path extending around the rotor shaft is sealed between the second seals, and the oil discharge path is constituted by a housing-side oil discharge groove and a shaft-side oil discharge groove arranged at a coaxial position. An annular seal tongue having a free end projecting into the annular oil discharge passage in the radial direction of the rotor shaft is provided in the discharge passage, and the seal tongue acts in an axial direction on the lubricant entering the oil discharge passage. This is solved by forming a barrier.

この結果、追加又は予備潤滑過程中に、特に吸込み（負圧）に関連し、潤滑油が軸受ハウジングから第２シール、そして流れ油排出路を経て第１シールに達するのを防ぐ。この結果、停止状態での油密性を高め、予測される運転条件下での漏れを防止できる。   As a result, during the additional or pre-lubricating process, in particular related to suction (negative pressure), the lubricating oil is prevented from reaching the first seal from the bearing housing via the second seal and the flow oil drain. As a result, it is possible to improve oil tightness in a stopped state and prevent leakage under predicted operating conditions.

ロータ軸の軸側油排出溝内にシール舌片を形成し、該舌片の半径方向外側自由端迄の高さが最大で特にタービンハウジングおよび／又は圧縮機ハウジングのハウジング孔の内周面と一致し、或いはそれより短いと好ましい。しかし、ハウジング側油排出溝内にシール舌片を形成し、その半径方向内側端迄の高さを、最大でハウジング孔の内周面と一致し、又はそれより短くなるよう形成してもよい。   A seal tongue is formed in the shaft-side oil discharge groove of the rotor shaft, and the height of the tongue to the radially outer free end is maximum, in particular the inner peripheral surface of the housing hole of the turbine housing and / or compressor housing It is preferable that they match or be shorter. However, a seal tongue piece may be formed in the housing-side oil discharge groove so that the height to the radially inner end thereof coincides with the inner peripheral surface of the housing hole at the maximum or shorter. .

また第２シールを、軸側油排出溝を境界づけ、半径方向外側に向けられハウジング孔の内周面に対して短くされた壁と、それと同軸位置に存在してハウジング側油排出溝を境界づけ半径方向内側に向けられハウジング孔の内周面に対して長くされた壁とで形成し、もつてその両壁で隙間を覆うとよい。即ち、ハウジング孔が、第２シールの軸方向位置で、成形されたシール舌片を有するロータ軸に達する直径より小さな直径を持つとよい。   In addition, the second seal is bounded by the shaft-side oil discharge groove, is a wall that is directed radially outward and shortened with respect to the inner peripheral surface of the housing hole, and is located at the same position as the wall to boundary the housing-side oil discharge groove. It is preferable to form a wall that is directed inward in the radial direction and is elongated with respect to the inner peripheral surface of the housing hole, and to cover the gap with both the walls. That is, the housing hole may have a diameter smaller than the diameter reaching the rotor shaft having the molded sealing tongue at the axial position of the second seal.

なお、シール舌片と壁が、別個の部品であるか否か、或いはハウジング又はロータ軸に旋盤加工部分或いはフライス加工部分として形成されたか否かは重要ではない。   It is not important whether the seal tongue and the wall are separate parts or whether they are formed as a lathe or milled part on the housing or rotor shaft.

排気駆動式過給機に利用する場合、潤滑材、即ち油が環状の油排出溝の円周を還流し、下部開口を介して流出するのを保証すべく、第２シールを軸方向において中央軸受ハウジングとタービンハウジング側軸受装置の第１シールとの間および／又は中央軸受ハウジングと圧縮機側軸受装置の第１シールとの間に配置するとよい。   When used in an exhaust-driven supercharger, the second seal is centered in the axial direction to ensure that the lubricant, i.e. oil, circulates around the circumference of the annular oil discharge groove and flows out through the lower opening. It may be arranged between the bearing housing and the first seal of the turbine housing side bearing device and / or between the central bearing housing and the first seal of the compressor side bearing device.

以下図を参照し、排気駆動式過給機の用途での本発明の実施例を詳細に説明する。   Embodiments of the present invention for use in an exhaust-driven supercharger will be described in detail below with reference to the drawings.

図１に示す如く、排気駆動式過給機は普通の如くタービンハウジング２と、該ハウジング２に結合された圧縮機ハウジング５を有し、両ハウジング２、３内にロータ軸１を備えている。内燃機関からの排気ガスをタービンランナ４に導入すべく、タービンハウジング２は略環状の排気ガス供給路２８を備える。かくして、ロータ軸１の他端に置かれた圧縮機インペラ７がロータ軸１を介して駆動される。この圧縮機インペラ７はそれを取り囲む供給路２９を介して空気を吸い込み、その空気を圧縮して吹き出す。   As shown in FIG. 1, the exhaust-drive supercharger has a turbine housing 2 and a compressor housing 5 coupled to the housing 2 as usual, and a rotor shaft 1 is provided in both housings 2 and 3. . In order to introduce exhaust gas from the internal combustion engine into the turbine runner 4, the turbine housing 2 includes a substantially annular exhaust gas supply path 28. Thus, the compressor impeller 7 placed at the other end of the rotor shaft 1 is driven via the rotor shaft 1. The compressor impeller 7 sucks air through a supply passage 29 surrounding the compressor impeller 7 and compresses and blows out the air.

ロータ軸１はタービンハウジング２内にハウジング孔３を通して案内され、そこでロー
タ軸端に、タービンランナ４が固定されている。通常、タービンハウジング２と圧縮機ハウジング５との間の中央軸受ハウジング１０内に、ロータ軸１の軸受１９、２０が存在する。該軸受１９、２０の潤滑材は、垂直の油供給ノズル２６およびそこから出ている油供給孔２７を介して加圧状態で供給される。 The rotor shaft 1 is guided through the housing hole 3 in the turbine housing 2, where a turbine runner 4 is fixed to the end of the rotor shaft. Usually, there are bearings 19, 20 for the rotor shaft 1 in the central bearing housing 10 between the turbine housing 2 and the compressor housing 5. The lubricant of the bearings 19 and 20 is supplied in a pressurized state through a vertical oil supply nozzle 26 and an oil supply hole 27 extending therefrom.

潤滑材が中央軸受ハウジング１０から、例えば軸受体１９と軸受ブッシュ２０とロータ軸１との間の軸受隙間を経てタービンハウジング２に到達するのを防止すべく、以下図２を参照して説明する密封装置を設けている。   In order to prevent the lubricant from reaching the turbine housing 2 from the central bearing housing 10 through, for example, a bearing gap between the bearing body 19, the bearing bush 20, and the rotor shaft 1, a description will be given below with reference to FIG. 2. A sealing device is provided.

好適には、タービンハウジング側軸受装置の内部の密封装置は、第１シール１１と第２シール１２を持つ（圧縮機ハウジング側軸受装置の密封装置も同様に形成されている）。これら第１、第２両シール１１、１２は、タービンハウジング２のハウジング壁と、ロータ軸１のラジアル軸受１９、２０の間に配置されている。該軸受は、公知の如く中央軸受ハウジング１０の軸受体１９を有し、該軸受体１９は軸受ブッシュ２０によってロータ軸１に結合している。軸受体１９とタービンハウジング２との間に、ロータ軸１の軸方向に延びる内部空間２１が存在し、該空間２１に、タービンハウジング２に向いて第２シール１２、次いでハウジンク側油排出溝１３が続いている。これは軸側油排出溝１４と共にロータ軸１の周りを延びる環状油排出路を形成している。この油排出路内にシール舌片１５が配置され、該舌片１５の自由端はロータ軸１の半径方向に環状油排出路１３、１４の中に突出している。このシール舌片１５に、軸方向に間隔を隔てて、タービンハウジング孔１の内周壁に接するピストンリングの形態の第１シール１１が続いている。   Preferably, the sealing device inside the turbine housing side bearing device has a first seal 11 and a second seal 12 (the sealing device of the compressor housing side bearing device is formed in the same manner). The first and second seals 11 and 12 are disposed between the housing wall of the turbine housing 2 and the radial bearings 19 and 20 of the rotor shaft 1. The bearing has a bearing body 19 of a central bearing housing 10 as is well known, and the bearing body 19 is coupled to the rotor shaft 1 by a bearing bush 20. An internal space 21 extending in the axial direction of the rotor shaft 1 exists between the bearing body 19 and the turbine housing 2, and the second seal 12 and then the housing side oil discharge groove 13 toward the turbine housing 2 are provided in the space 21. It is continuing. This forms an annular oil discharge passage that extends around the rotor shaft 1 together with the shaft-side oil discharge groove 14. A seal tongue 15 is disposed in the oil discharge passage, and a free end of the tongue 15 projects into the annular oil discharge passages 13 and 14 in the radial direction of the rotor shaft 1. The seal tongue 15 is followed by a first seal 11 in the form of a piston ring that is in contact with the inner peripheral wall of the turbine housing hole 1 at an axial interval.

ピストンリング１１は、場合により侵入する流体を漏れ止めすべく、ロータ軸１又はこれに結合された回転部品の溝１８にはめ込まれている。シール舌片１５はロータ軸１の軸側油排出溝１４内に形成され、舌片１５の半怪方向外側端迄の高さは、最大でタービンハウジング２のハウシング孔３の内周面と−致するか、図示の如く幾分短くされている。   The piston ring 11 is fitted in the rotor shaft 1 or a groove 18 of a rotating part coupled to the rotor shaft 1 in order to prevent leakage of intruding fluid. The seal tongue 15 is formed in the shaft-side oil discharge groove 14 of the rotor shaft 1, and the height of the tongue 15 to the outer half end in the half mysterious direction is a maximum with the inner peripheral surface of the housing hole 3 of the turbine housing 2. It matches or is somewhat shortened as shown.

しかし、シール舌片１５をハウジング側油排出溝１３内に配置し、その半径方向内側端迄の高さを、最大でタービンハウジング２のハウジング孔３の内周面と一致するか、或いはそれより幾分短く形成してもよい。この関係で、ハウジング側油排出溝と軸側油排出溝に、各々半径方向において重なり相互作用するシール舌片を設けてもよい。   However, the seal tongue 15 is disposed in the housing side oil discharge groove 13, and its height to the radially inner end coincides with the inner peripheral surface of the housing hole 3 of the turbine housing 2 at the maximum, or more It may be formed somewhat short. In this relationship, the housing side oil discharge groove and the shaft side oil discharge groove may be provided with seal tongues that overlap and interact in the radial direction.

第２シール１２を形成すべく、軸側油排出溝１４が、タービンランナ４とは反対側に位置し、半径方向外側に向いて延びかつタービンハウジング孔３の内周面より短くされた壁３１で形成され、更にハウジング側油排出溝１３が、タービンランナ４とは反対側に位置し、半径方向内側に向いて延び、かつタービンハウジング孔３の内周面より長い壁３２で形成されている。両壁３１、３２は隙間３３を封じ込め、潤滑材が隙間３３を通り、油排出路１３、１４を越えて第１シール１１迄継続して流出するのを防止すべくシール舌片１５の自由端は半径方向において前記隙間３３と重なり合っている。   In order to form the second seal 12, the shaft-side oil discharge groove 14 is located on the opposite side of the turbine runner 4, extends radially outward, and is shorter than the inner peripheral surface of the turbine housing hole 3. Further, the housing side oil discharge groove 13 is located on the side opposite to the turbine runner 4, extends inward in the radial direction, and is formed by a wall 32 longer than the inner peripheral surface of the turbine housing hole 3. . Both walls 31, 32 contain a gap 33, and the free end of the seal tongue 15 prevents the lubricant from passing through the gap 33 and continuing to flow out to the first seal 11 over the oil discharge passages 13, 14. Overlaps the gap 33 in the radial direction.

第２シール１２の隙間３３を通り、例えばシール舌片１５に付着した潤滑材の液滴が、吸込みによって更に第１シール１１のピストンリング迄達するのを防止すべく、シール舌片１５の自由端を対応したハウジング孔３或いはハウジング孔６の内周面に対し、例えば４５゜の角度を成して形成している。   In order to prevent, for example, a droplet of lubricant that has passed through the gap 33 of the second seal 12 and adhered to the seal tongue 15 from reaching the piston ring of the first seal 11 due to suction, the free end of the seal tongue 15 is prevented. Is formed at an angle of 45 °, for example, with respect to the inner peripheral surface of the corresponding housing hole 3 or housing hole 6.

上述した実施例は所定の組立様式に適合される。即ち、ロータ軸１をまずタービンハウジング２を通して差込み、次いで中央軸受ハウジング１０に差込み、圧縮機ハウジング５内で圧縮機インペラ７をロータ軸先端部上にはめ込むようにできる。   The embodiment described above is adapted to a predetermined assembly mode. That is, the rotor shaft 1 can be inserted first through the turbine housing 2 and then into the central bearing housing 10 so that the compressor impeller 7 can be fitted on the rotor shaft tip in the compressor housing 5.

これが可能な理由は、図示の実施例において、シール舌片１５の高さ（矢印ａ）がハウジング孔の内周面（矢印ｂ）から突出する必要がなく、短い壁３１（矢印ｃ）と長い壁３２（矢印ｄ）が隙間３３を境界づけ、タービンハウジング２内でのロータ軸１の直径が、第２シール１２の範囲でのロータ軸１の直径より大きく、かつ第２シール１２の範囲でのロータ軸１の直径が、この実施例における中央軸受ハウジング１０のロータ軸の直径より大きくなっていることにある。即ちシール舌片１５は、隙間３３を軸方向に覆って油排出路１３、１４に潤滑油が侵入しないようにすべく、ロータ軸１の半径方向にできるだけ大きな高さで形成せねばならないが、タービン側ハウジング孔３の内周面を越える必要はなく、従ってロータ軸１は組立可能である   The reason why this is possible is that in the illustrated embodiment, the height of the seal tongue 15 (arrow a) does not need to protrude from the inner peripheral surface (arrow b) of the housing hole, and the length of the short wall 31 (arrow c) is long. The wall 32 (arrow d) bounds the gap 33, the diameter of the rotor shaft 1 in the turbine housing 2 is larger than the diameter of the rotor shaft 1 in the range of the second seal 12, and in the range of the second seal 12. The diameter of the rotor shaft 1 is larger than the diameter of the rotor shaft of the central bearing housing 10 in this embodiment. That is, the seal tongue 15 must be formed as high as possible in the radial direction of the rotor shaft 1 so as to cover the gap 33 in the axial direction and prevent the lubricating oil from entering the oil discharge passages 13 and 14. It is not necessary to exceed the inner peripheral surface of the turbine side housing hole 3, and therefore the rotor shaft 1 can be assembled.

排気駆動式過給機の主要部の軸断面図。The axial sectional view of the principal part of an exhaust drive supercharger. タービンハウジング側軸受装置の内部におけるロータ軸の本発明に基づく密封装置の図１におけるＸ部の拡大詳細図。FIG. 2 is an enlarged detailed view of a portion X in FIG. 1 of the sealing device according to the present invention of the rotor shaft inside the turbine housing side bearing device.

符号の説明Explanation of symbols

１ ロータ軸、２ タービンハウジング、３ ハウジング孔、４ タービンランナ、５ 圧縮機ハウジング、７ 圧縮機インペラ、１１、１２ シール、１３ ハウジング側油排出溝、１４ 軸側油排出溝、１５ シール舌片、３１、３２ 壁、３３ 隙間

DESCRIPTION OF SYMBOLS 1 Rotor shaft, 2 Turbine housing, 3 Housing hole, 4 Turbine runner, 5 Compressor housing, 7 Compressor impeller, 11, 12 Seal, 13 Housing side oil discharge groove, 14 Shaft side oil discharge groove, 15 Seal tongue, 31, 32 wall, 33 gap

Claims (9)

導入された潤滑材に対し軸受ハウジンクを軸方向に密封する軸受の密封装置において、
ロータ軸（１）に、隙間、ラビリンス又はピストンリングの形態の第１シール（１１）と、狭い隙間（３３）やラビリンスの形をした第２シール（１２）が設けられ、該第１、第２シール（１１、１２）間に、ロータ軸（１）の周りに延びる油排出路（１３、１４）が封じ込められ、該油排出路（１３、１４）が、ハウジング側油排出溝（１３）と同軸位置に配置された軸側油排出溝（１４）として構成され、前記油排出路（１３、１４）内に、ロータ軸（Ｔ）の半径方向にその自由端が環状油排出路（１３、１４）の中に突出する環状シール舌片（１５）が設けられ、このシール舌片（１５）が油排出路に侵入する潤滑材に対して軸方向に作用するバリアを形成することを特徴とする密封装置。 In the bearing sealing device for axially sealing the bearing housing against the introduced lubricant,
The rotor shaft (1) is provided with a first seal (11) in the form of a gap, a labyrinth or a piston ring and a second seal (12) in the form of a narrow gap (33) or a labyrinth. Between the two seals (11, 12), the oil discharge passages (13, 14) extending around the rotor shaft (1) are enclosed, and the oil discharge passages (13, 14) serve as housing side oil discharge grooves (13). And is arranged as a shaft-side oil discharge groove (14) arranged coaxially with the oil discharge passage (13, 14) in the radial direction of the rotor shaft (T), the free end of which is an annular oil discharge passage (13 , 14) is provided with a projecting annular seal tongue (15), and this seal tongue (15) forms a barrier acting in the axial direction against the lubricant entering the oil discharge passage. Sealing device. ロータ軸（ｌ）がタービンハウジング（２）内でハウジング孔（３）を経て案内される片側端にタービンランナ（４）を支持し、圧縮機ハウジング（５）内でハウジング孔を経て案内される反対側端に圧縮機インペラ（７）を支持する排気駆動式過給機に利用され、タービンハウジング（２）および／又は圧縮機ハウジング（５）を、タービンハウジング（２）と圧縮機ハウジング（５）の間の中央軸受ハウジング（１０）から出て、タービンハウジング側軸受装置および／又は圧縮機ハウジング側軸受装置に導かれる潤滑材に対し密封すべく、ロータ軸（１）のタービンハウジング側軸受装置および／又は圧縮機ハウジング側軸受装置内に密封装置が設けられたことを特徴とする請求項１記載の密封装置。   The rotor shaft (1) supports the turbine runner (4) at one end guided through the housing hole (3) in the turbine housing (2), and is guided through the housing hole in the compressor housing (5). Used in an exhaust-driven supercharger that supports a compressor impeller (7) at the opposite end, the turbine housing (2) and / or the compressor housing (5), the turbine housing (2) and the compressor housing (5 The turbine housing side bearing device of the rotor shaft (1) to seal against the lubricant guided out of the central bearing housing (10) between the turbine housing side bearing device and / or the compressor housing side bearing device The sealing device according to claim 1, wherein a sealing device is provided in the bearing device on the compressor housing side. ロータ軸（１）の軸側油排出溝（１４）内にシール舌片（１５）が形成され、該舌片の半径方向外側自由端迄の高さが、最大で特にタービンハウジング（２）および／又は圧縮機ハウジング（５）のハウジング孔（３、６）の内周面と一致し、或いはそれより短く形
成されたことを特徴とする請求項１又は２記載の密封装置。 A seal tongue (15) is formed in the shaft-side oil discharge groove (14) of the rotor shaft (1), the height of the tongue to the radially outer free end being maximum, in particular the turbine housing (2) and 3. The sealing device according to claim 1, wherein the sealing device is formed so as to coincide with or shorter than the inner peripheral surface of the housing hole (3, 6) of the compressor housing (5). ハウジング側油排出溝（１３）内にシール舌片（１５）が形成され、該シール舌片の半径方向内側端迄の高さが、最大で特にタービンハウジング（２）および／又は圧縮機ハウジング（５）のハウジング孔（３、６）の内周面と一致し、或いはそれより短く形成されたことを特徴とする請求項１又は２記載の密封装置。   A seal tongue (15) is formed in the housing side oil discharge groove (13), and the height of the seal tongue to the radially inner end is at most a turbine housing (2) and / or a compressor housing ( The sealing device according to claim 1 or 2, wherein the sealing device is formed so as to coincide with or shorter than the inner peripheral surface of the housing hole (5, 6). 第２シール（１２）が、軸側油排出溝（１４）を境界づけ、半径方向外側に向き、ハウジング孔（３および／又は６）の内周面に対し短い壁（３１）と、それと同軸位置に存在してハウジング側油排出溝（１３）を境界づけ半径方向内側に向き、ハウジング孔（３および／又は６）の内周面に対し長い壁（３２）とで形成され、該両壁（３１、３２）が隙間（３３）を封じ込め、シール舌片（１５）の自由端が隙間（３３）と半径方向において重畳していることを特徴とする請求項１から４の１つに記載の密封装置。   The second seal (12) bounds the axial oil discharge groove (14), faces radially outward, and is short with respect to the inner peripheral surface of the housing hole (3 and / or 6), and is coaxial with the short wall (31) The wall is formed with a wall (32) which is located at a position and borders the housing side oil discharge groove (13) and faces radially inward, and is long with respect to the inner peripheral surface of the housing hole (3 and / or 6). One of claims 1 to 4, characterized in that (31, 32) contain the gap (33) and the free end of the sealing tongue (15) overlaps the gap (33) in the radial direction. Sealing device. 第１シール（１１）がラビリンスパッキンとして形成されたことを特徴とする請求項１から５の１つに記載の密封装置。   6. Sealing device according to claim 1, wherein the first seal (11) is formed as a labyrinth packing. 第１シール（１１）がハウジング孔（３および／又は）内周面に接するピストンリングの形に形成されたことを特徴とする請求項１から５の１つに記載の密封装置。   6. Sealing device according to claim 1, characterized in that the first seal (11) is formed in the form of a piston ring in contact with the inner peripheral surface of the housing bore (3 and / or). ピストンリング（１１）が、ロータ軸（１）或いはこのロータ軸（１）に結合された回転部品の溝（１８）にはめ込まれたことを特徴とする請求項７記載の密封装置。   8. Sealing device according to claim 7, characterized in that the piston ring (11) is fitted in the rotor shaft (1) or in the groove (18) of the rotating part connected to the rotor shaft (1). シール舌片（１５）の自由端が、対応するハウジング孔（３、６）の内周面に対し傾斜していることを特徴とする請求項１から８の１つに記載の密封装置。   9. The sealing device according to claim 1, wherein the free end of the sealing tongue (15) is inclined with respect to the inner peripheral surface of the corresponding housing hole (3, 6).
JP2005329970A 2004-11-17 2005-11-15 Bearing sealing device Pending JP2006145034A (en)

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Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2009167803A (en) * 2008-01-10 2009-07-30 Jtekt Corp Supercharger
JP2010530491A (en) * 2007-06-18 2010-09-09 コンチネンタル オートモーティヴ ゲゼルシャフト ミット ベシュレンクテル ハフツング Vehicle turbocharger with unique sealing device
JP2011220338A (en) * 2010-04-09 2011-11-04 Abb Turbo Systems Ag Shaft seal
WO2014209852A1 (en) * 2013-06-28 2014-12-31 Borgwarner Inc. Turbocharger compressor-end carbon face seal
CN105370325A (en) * 2014-08-08 2016-03-02 曼柴油机和涡轮机欧洲股份公司 Shaft sealing system and exhaust gas turbocharger

Families Citing this family (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB0623705D0 (en) 2006-11-28 2007-01-10 Cummins Turbo Tech Ltd Hydraulic for a turbocharger
US20130106061A1 (en) * 2011-10-28 2013-05-02 General Electric Company High temperature seal system
CN102996650B (en) * 2012-11-26 2015-01-07 北京七星华创电子股份有限公司 Gas sealing device for low-speed rotation of main shaft
KR101536061B1 (en) 2012-12-14 2015-07-10 에이비비 터보 시스템즈 아게 Shaft seal
JP6097188B2 (en) * 2013-09-25 2017-03-15 三菱重工業株式会社 Turbocharger
FR3020658B1 (en) * 2014-04-30 2020-05-15 Safran Aircraft Engines LUBRICATION OIL RECOVERY HOOD FOR TURBOMACHINE EQUIPMENT
US9988976B2 (en) * 2014-05-24 2018-06-05 Honeywell International Inc. Turbocharger
FR3022587B1 (en) * 2014-06-23 2019-03-22 Safran Aircraft Engines DEVICE AND METHOD FOR LUBRICATING A TURBOMACHINE BEARING BEARING
US10196986B2 (en) * 2015-09-04 2019-02-05 General Electric Company Hydrodynamic seals in bearing compartments of gas turbine engines
DE102018106900A1 (en) * 2018-03-22 2019-09-26 Man Energy Solutions Se Turbo compressor
TWI735960B (en) * 2018-09-28 2021-08-11 美商英普羅密封有限責任公司 Shaft seal assembly
DE102019101258A1 (en) 2019-01-18 2020-07-23 Bayerische Motoren Werke Aktiengesellschaft Exhaust gas turbocharger

Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5290759A (en) * 1976-01-23 1977-07-30 Hitachi Ltd Shaft sealing device
JPS5353262A (en) * 1976-10-25 1978-05-15 Mitsubishi Electric Corp Manufacture of semiconductor device
JPS5720518A (en) * 1980-07-14 1982-02-03 Aisin Seiki Co Ltd Turbocharger
JPS59119026A (en) * 1982-12-24 1984-07-10 Aisin Seiki Co Ltd Seal device for turbo charger
JPS6014246A (en) * 1983-07-06 1985-01-24 Dainippon Printing Co Ltd Photoengraving system for video image
JPH0389080A (en) * 1989-08-30 1991-04-15 Ebara Corp Seal mechanism for vacuum pump lubricating oil
JPH0417572A (en) * 1990-05-10 1992-01-22 Mitsubishi Electric Corp Inverter discharger
JPH05332456A (en) * 1992-05-28 1993-12-14 Daikin Ind Ltd Seal structure of rotating member and assembling method and sealing method thereof
JP2002130485A (en) * 2000-08-31 2002-05-09 Atlas Copco Comptec Inc Liquid seal

Family Cites Families (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE848504C (en) * 1942-03-07 1952-09-04 Borsig Ag Device for shaft sealing of centrifugal machines, preferably turbines, by means of labyrinth sealing bushes
DE1775833A1 (en) * 1968-09-30 1971-09-23 Bergmann Borsig Veb Non-contact shaft seal, especially for turbines
US3630529A (en) * 1969-05-05 1971-12-28 Borg Warner Sodium vapor trap
DE2220608A1 (en) * 1972-04-27 1973-11-08 Fendt & Co Xaver SEAL ARRANGEMENT ON ROTATING MACHINE PARTS SUCH AS ON A WORKING SPINDLE OF MACHINE TOOLS
DE2260686C3 (en) * 1972-12-12 1978-06-29 Pohlig-Heckel-Bleichert, Vereinigte Maschinenfabriken Ag, 5000 Koeln Sealing of a rolling bearing
CH582319A5 (en) * 1975-03-05 1976-11-30 Bbc Brown Boveri & Cie
US4268229A (en) * 1979-04-19 1981-05-19 The Garrett Corporation Turbocharger shaft seal arrangement
JPH01285699A (en) * 1988-05-12 1989-11-16 Nippon Seiko Kk Sealed device for water pump bearing
GB2234788A (en) * 1989-08-03 1991-02-13 Crane John Uk Ltd Mechanical face seal
DE4221241A1 (en) * 1991-07-09 1993-02-11 Otto Dipl Ing Kraic Seal on a rotating body and - points providing minimum clearance distributed in series along inner or outer periphery of seal ring
DE4403776C2 (en) * 1994-02-01 1998-04-09 Aeg Westinghouse Transport Seal with labyrinthine sealing gap
DE19745659C1 (en) * 1997-10-17 1999-05-06 Man B & W Diesel Ag Turbo-supercharger for internal combustion engine
DE19818873C2 (en) * 1998-04-28 2001-07-05 Man B & W Diesel Ag Reciprocating internal combustion engine
DE10011063A1 (en) * 2000-03-07 2001-09-27 Daimler Chrysler Ag Labyrinth seal for shaft of electric motor is made up of two sections, outer section having annular components which form conical seal gaps with surface of other component

Patent Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5290759A (en) * 1976-01-23 1977-07-30 Hitachi Ltd Shaft sealing device
JPS5353262A (en) * 1976-10-25 1978-05-15 Mitsubishi Electric Corp Manufacture of semiconductor device
JPS5720518A (en) * 1980-07-14 1982-02-03 Aisin Seiki Co Ltd Turbocharger
JPS59119026A (en) * 1982-12-24 1984-07-10 Aisin Seiki Co Ltd Seal device for turbo charger
JPS6014246A (en) * 1983-07-06 1985-01-24 Dainippon Printing Co Ltd Photoengraving system for video image
JPH0389080A (en) * 1989-08-30 1991-04-15 Ebara Corp Seal mechanism for vacuum pump lubricating oil
JPH0417572A (en) * 1990-05-10 1992-01-22 Mitsubishi Electric Corp Inverter discharger
JPH05332456A (en) * 1992-05-28 1993-12-14 Daikin Ind Ltd Seal structure of rotating member and assembling method and sealing method thereof
JP2002130485A (en) * 2000-08-31 2002-05-09 Atlas Copco Comptec Inc Liquid seal

Cited By (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2010530491A (en) * 2007-06-18 2010-09-09 コンチネンタル オートモーティヴ ゲゼルシャフト ミット ベシュレンクテル ハフツング Vehicle turbocharger with unique sealing device
JP2009167803A (en) * 2008-01-10 2009-07-30 Jtekt Corp Supercharger
JP2011220338A (en) * 2010-04-09 2011-11-04 Abb Turbo Systems Ag Shaft seal
WO2014209852A1 (en) * 2013-06-28 2014-12-31 Borgwarner Inc. Turbocharger compressor-end carbon face seal
GB2530699A (en) * 2013-06-28 2016-03-30 Borgwarner Inc Turbocharger compressor-end carbon face seal
GB2530699B (en) * 2013-06-28 2016-09-21 Borgwarner Inc Turbocharger compressor-end carbon face seal
CN105370325A (en) * 2014-08-08 2016-03-02 曼柴油机和涡轮机欧洲股份公司 Shaft sealing system and exhaust gas turbocharger
JP2016037960A (en) * 2014-08-08 2016-03-22 マン・ディーゼル・アンド・ターボ・エスイー Shaft seal system and exhaust gas turbocharger

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FR2878007B1 (en) 2014-09-12
GB2420602A (en) 2006-05-31
DE102004055429B3 (en) 2006-08-10
CN1776264A (en) 2006-05-24
FR2878007A1 (en) 2006-05-19
GB2420602B (en) 2009-03-18
GB0523192D0 (en) 2005-12-21
CN1776264B (en) 2010-06-16
CH698162B1 (en) 2009-06-15

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