EP2772652A2 - Paroi intermédiaire pour isoler de façon étanche l'espace arrière d'un compresseur radial - Google Patents

Paroi intermédiaire pour isoler de façon étanche l'espace arrière d'un compresseur radial Download PDF

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Publication number
EP2772652A2
EP2772652A2 EP14155860.1A EP14155860A EP2772652A2 EP 2772652 A2 EP2772652 A2 EP 2772652A2 EP 14155860 A EP14155860 A EP 14155860A EP 2772652 A2 EP2772652 A2 EP 2772652A2
Authority
EP
European Patent Office
Prior art keywords
intermediate wall
bearing housing
compressor
bearing
sealing
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
Application number
EP14155860.1A
Other languages
German (de)
English (en)
Other versions
EP2772652A3 (fr
EP2772652B1 (fr
Inventor
Andrea Vacca
Matthias Jarusel
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.)
Turbo Systems Switzerland Ltd
Original Assignee
ABB Turbo Systems AG
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 ABB Turbo Systems AG filed Critical ABB Turbo Systems AG
Publication of EP2772652A2 publication Critical patent/EP2772652A2/fr
Publication of EP2772652A3 publication Critical patent/EP2772652A3/fr
Application granted granted Critical
Publication of EP2772652B1 publication Critical patent/EP2772652B1/fr
Active legal-status Critical Current
Anticipated expiration legal-status Critical

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Classifications

    • 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
    • F01D11/00—Preventing or minimising internal leakage of working-fluid, e.g. between stages
    • F01D11/02—Preventing or minimising internal leakage of working-fluid, e.g. between stages by non-contact sealings, e.g. of labyrinth type
    • F01D11/04—Preventing or minimising internal leakage of working-fluid, e.g. between stages by non-contact sealings, e.g. of labyrinth type using sealing fluid, e.g. steam
    • 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
    • F04D29/05—Shafts or bearings, or assemblies thereof, specially adapted for elastic fluid pumps
    • F04D29/056—Bearings
    • 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
    • F04D29/102—Shaft sealings especially adapted for elastic fluid pumps
    • 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
    • F01D5/00—Blades; Blade-carrying members; Heating, heat-insulating, cooling or antivibration means on the blades or the members
    • F01D5/02—Blade-carrying members, e.g. rotors
    • F01D5/04—Blade-carrying members, e.g. rotors for radial-flow machines or engines
    • F01D5/043—Blade-carrying members, e.g. rotors for radial-flow machines or engines of the axial inlet- radial outlet, or vice versa, type
    • 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
    • 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
    • F05D2260/00—Function
    • F05D2260/60—Fluid transfer
    • F05D2260/602—Drainage
    • F05D2260/6022—Drainage of leakage having past a seal

Definitions

  • the invention relates to the field of exhaust gas turbochargers of supercharged internal combustion engines.
  • It relates to an intermediate wall for sealing the rear space of the compressor wheel of a centrifugal compressor with respect to a bearing space enclosed by a bearing housing, a bearing device for supporting the rotor of a compressor with such a partition, a centrifugal compressor with such a bearing device and an exhaust gas turbocharger with such a centrifugal compressor.
  • Exhaust gas turbochargers are used to increase the performance of internal combustion engines.
  • the exhaust gas turbine of the exhaust gas turbocharger is charged with the exhaust gases of the internal combustion engine and their kinetic energy used for sucking and compressing air for the internal combustion engine.
  • the impellers of the turbine and the compressor are connected to each other via a shaft mounted in a bearing housing shaft.
  • sealing air is often used to protect the storage area from penetrating hot exhaust gases from the flow channel or to actively cool the turbine wheel.
  • This barrier air may be externally supplied or removed from the airflow downstream of the compressor.
  • sealing air can also be discharged from the rear space of the compressor wheel, which brings about the positive effect of relieving the axial load on the compressor wheel, since the pressure in the rear space of the compressor wheel is reduced due to the discharge of the sealing air.
  • the air in the rear space of the compressor wheel penetrates from the flow channel of the compressor wheel in this area, since the gap between the rapidly rotating and larger temperature fluctuations exposed compressor wheel can not seal arbitrarily well.
  • the air discharged in this way is guided through several components to the turbine side. This results in housing transitions, which must be sealed against leakage of the sealing air.
  • the at least one barrier air transition between the immediately adjacent to the Verêtrrad Wegraum intermediate wall and the bearing housing has hitherto been realized by means of a respective round pin, which was brought to the partition and was received in a corresponding opening in the bearing housing.
  • the at least one pin on the otherwise essentially rotationally symmetrical intermediate wall was produced by the complex machining method of circular milling.
  • the object of the invention is to optimize the intermediate wall for sealing the rear space of the compressor wheel of a centrifugal compressor, which has at least one bore for Sperr Kunststoffab Installation, with respect to a simplified production.
  • the intermediate wall has a circumferential, rotationally symmetrical shaped mounting flange which is provided for fastening the intermediate wall to the adjacent bearing housing and which has a planar contact surface for resting on a contact surface of the bearing housing.
  • a plurality of bores are embedded in a virtual circular line in the mounting flange, wherein the bores comprise at least one sealing air channel and a plurality of circumferentially distributed on the virtual circle arranged holes for receiving fasteners.
  • the intermediate wall is designed as a rotationally symmetrical disk, which can be brought into its final shape in production by the machining process of turning and without further milling.
  • a drill is necessary, which can also be used for drilling the holes for receiving the fasteners.
  • Fig. 1 shows an exhaust gas turbocharger according to the prior art with an axially flowed exhaust gas turbine 10 and a centrifugal compressor 70.
  • the partially cut exhaust gas turbocharger has a rotor consisting of turbine wheel 11, compressor 71 and intermediate shaft 20 on.
  • the rotor is rotatably mounted in the bearing housing 30.
  • the exhaust gas originating from the combustion chambers of an internal combustion engine is guided through the gas inlet housing 12 onto the rotor blades of the turbine wheel 11. Subsequently, the exhaust gas is collected in the diffuser region of the gas outlet housing 13 and discharged via the exhaust system.
  • the compressor wheel driven by the turbine via the shaft draws in fresh air in order to compress it and supply it under higher pressure to the combustion chambers of the internal combustion engine.
  • sealing air is often used on the turbine side to protect the storage area from penetrating hot exhaust or to cool the turbine hub.
  • This sealing air is usually a Beitechnische the Verêtrradschubentlastung, in which the air pressure in the rear space the compressor wheel is reduced by the air from the flow channel of the compressor in this area penetrating air is removed.
  • Fig. 2 shows a guided along the shaft axis section through the centrifugal compressor of an exhaust gas turbocharger.
  • the compressor wheel 71 is arranged in the compressor housing 72.
  • the compressor wheel comprises a hub body and a plurality of blades.
  • a seal which is usually designed as a labyrinth seal. This seal ensures that no larger amount of fresh air under increased pressure escapes from the flow channel at the outlet of the compressor wheel in the rear space of the compressor wheel.
  • To the bearing housing 30 towards the rear space is limited by a disc-shaped partition 40.
  • the intermediate wall has a central opening in the interior, through which the shaft 20 is guided.
  • part of the compressor wheel 71 may project into or through the central opening in the intermediate wall. Between the rotor and the intermediate wall a bidirectionally effective sealing point is provided in the radially inner region. On the one hand, it should be prevented that too much fresh air escapes from the rear space of the compressor wheel into the storage area under ambient pressure (blow-by). On the other hand, it should be prevented that at certain operating points of the compressor in reverse pressure conditions, oil or oil-laden air can pass from the storage area in the rear space of the compressor wheel.
  • the intermediate wall is mounted in the radially outer region of the bearing housing and the transition is also secured with a seal 35.
  • the disc-shaped intermediate wall 40 has on the side facing the bearing area a circumferential mounting flange 41 which is provided according to the invention for support on a likewise circumferential mounting flange 31 of the bearing housing. Between intermediate wall 40 and bearing housing 30 results radially outside the peripheral flanges, a cavity 36 which can be used for cooling the housing portion at the outer edge or at the outlet of the compressor wheel. For example, a cooling medium (water or cool air) can be passed through the cavity.
  • a cooling medium water or cool air
  • the intermediate wall 41 several continuous openings are recessed in the region of the mounting flange, which are each either as a sealing air passage 42 of the discharge of sealing air from the rear space of the compressor wheel ( Fig. 2 , upper half), or as a bore 43 of the mounting of fastening means 50 (FIG. Fig. 2 , lower half).
  • a sealing air passage 42 of the discharge of sealing air from the rear space of the compressor wheel Fig. 2 , upper half
  • a bore 43 of the mounting of fastening means 50 FIG. Fig. 2 , lower half.
  • the bearing surfaces of the two flanges are formed in the illustrated embodiment as axial end faces and extend in a plane perpendicular to the axis.
  • the bearing surfaces may also be slightly conically aligned, wherein the bearing surfaces of the two flanges are strictly parallel to each other.
  • a sealing point 34 is located radially inside the openings arranged on a circle.
  • the groove on one side either in the bearing surface of the flange 41 of the intermediate wall, or - as in the illustrated embodiment - be embedded in the bearing surface of the flange 31 on the bearing housing, or on both sides in both bearing surfaces.
  • the sealing ring a conventional O-ring, is squeezed when placing the intermediate wall on the bearing housing in the axial direction in the groove and thus seals between the two opposite bearing surfaces.
  • the sealing air channel is sealed off from the storage area, so that no blow-by flow escapes into the storage area.
  • the fasteners are sealed according to the invention, so that in the above-mentioned operating point with reversed pressure ratios no oil or oil-laden air can pass from the storage area in the rear space of the compressor wheel.
  • the bores for receiving the fastening means may have the same diameter as the bore of the sealing air channel for receiving a screw head to a residual depth with a smaller diameter. This facilitates the production of the intermediate wall.
  • the arrangement of the two types of holes may be regular or irregular.
  • the fastening means 50 are regularly distributed along the circumference.
  • the at least one barrier air channel 42 may instead of as shown a fastening opening, or additionally arranged between two spaced apart attachment openings.
  • Fig. 3 shows a view in the axial direction of the intermediate wall 40 in the in Fig. 2 indicated, guided along III-III section through the rear space portion of the centrifugal compressor.
  • the depressions of the labyrinth seal 44 are indicated by a plurality of concentric circles.
  • the shaft 20 and the shaft enclosing, cylindrical extension of the compressor wheel is shown.
  • FIG. 4 shows partition wall and bearing housing along the in Fig. 2 indicated, along IV-IV guided section through the rear space region of the centrifugal compressor Fig. 2 , In this case, the bearing housing 30 is cut in the radially outer region. Subsequently, the section passes through the enclosed between the intermediate wall and the bearing housing cavity 36, which can optionally be used to cool the housing portion at the compressor wheel outlet.
  • the cavity 36 is bounded by the flange 31, in which according to the invention the bores 33 and at least one sealing air channel 32 are arranged.
  • the sealing point 34 can be seen, which extends in the region of the flange 31 but radially within the sealing air channel 32 and holes 33.
  • the shaft 20 In the radially innermost region, in turn, the shaft 20, the extension of the compressor wheel 71 and a piece of the in this area inclined to the bearing side intermediate wall 40 is indicated.
  • the intermediate wall 40 is according to the invention, despite existing sealing air feedthrough, a rotationally symmetrical disc, which can be brought into production by turning and without milling in its final form.
  • a drill is necessary, which can also be used for drilling the holes for receiving the fasteners.
  • the manufacturing process can be simplified compared to a conventional partition.
  • the intermediate wall has an additional positioning hole, which is provided for receiving a positioning pin, which on the bearing housing is mounted or introduced before mounting in a designated positioning hole in the bearing housing.
  • the positioning can be realized by an irregular distribution of the holes for receiving the fastening means.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
  • Supercharger (AREA)
EP14155860.1A 2013-02-28 2014-02-20 Paroi intermédiaire pour isoler de façon étanche l'espace arrière d'un compresseur radial Active EP2772652B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102013203455.5A DE102013203455A1 (de) 2013-02-28 2013-02-28 Zwischenwand zur Abdichtung des Rückraums eines Radialverdichters

Publications (3)

Publication Number Publication Date
EP2772652A2 true EP2772652A2 (fr) 2014-09-03
EP2772652A3 EP2772652A3 (fr) 2018-03-28
EP2772652B1 EP2772652B1 (fr) 2021-10-06

Family

ID=50137527

Family Applications (1)

Application Number Title Priority Date Filing Date
EP14155860.1A Active EP2772652B1 (fr) 2013-02-28 2014-02-20 Paroi intermédiaire pour isoler de façon étanche l'espace arrière d'un compresseur radial

Country Status (5)

Country Link
EP (1) EP2772652B1 (fr)
JP (1) JP5850965B2 (fr)
KR (1) KR101617938B1 (fr)
CN (1) CN104018933B (fr)
DE (1) DE102013203455A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN109209520A (zh) * 2018-09-13 2019-01-15 中国科学院工程热物理研究所 一种向心涡轮背部空腔泄漏流损失抑制密封技术

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102015005054A1 (de) * 2015-04-21 2016-10-27 Man Diesel & Turbo Se Strömungsmaschine
DE102017208117A1 (de) * 2017-05-15 2018-11-15 Man Diesel & Turbo Se Turbolader
US20190277159A1 (en) * 2018-03-09 2019-09-12 GM Global Technology Operations LLC Turbocharger assembly

Family Cites Families (17)

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Publication number Priority date Publication date Assignee Title
CN1030342C (zh) * 1992-08-03 1995-11-22 亚瑞亚·勃朗勃威力有限公司 废气涡轮增压器
DE4225625A1 (de) * 1992-08-03 1994-02-10 Asea Brown Boveri Abgasturbolader
JPH06346749A (ja) * 1993-06-04 1994-12-20 Mitsubishi Heavy Ind Ltd 排気タービン過給機
JP3606293B2 (ja) * 1996-02-14 2005-01-05 石川島播磨重工業株式会社 排気タービン過給機
EP0903465B1 (fr) * 1997-09-19 2003-09-03 ABB Turbo Systems AG Connexion entre roue de compresseur et arbre pour turbomachines à haute vitesse
DE19845375A1 (de) * 1998-10-02 2000-04-06 Asea Brown Boveri Verfahren und Vorrichtung zur indirekten Kühlung der Strömung in zwischen Rotoren und Statoren von Turbomaschinen ausgebildeten Radialspalten
KR100339827B1 (ko) * 1999-07-22 2002-06-07 이종식 폐합성수지 연소장치
DE59913001D1 (de) * 1999-10-20 2006-02-02 Abb Turbo Systems Ag Baden Verfahren und vorrichtung zur indirekten kühlung der strömung in zwischen rotoren und statoren von turbomaschinen ausgebildeten radialspalten
JP2002180841A (ja) * 2000-12-14 2002-06-26 Toyota Motor Corp ターボコンプレッサ及びターボチャージャ
CN1329629C (zh) * 2002-05-06 2007-08-01 Abb涡轮系统有限公司 将工作轮固定在轴上的固定装置
JP4539487B2 (ja) * 2005-08-05 2010-09-08 株式会社Ｉｈｉ 電動機付過給機
DE102006048784A1 (de) * 2006-10-12 2008-04-17 Man Diesel Se Verdichter für einen Turbolader sowie Verfahren zu dessen Kühlung
EP2067999A1 (fr) * 2007-12-06 2009-06-10 Napier Turbochargers Limited Rotor de turbocompresseur de suralimentation refroidi par liquide et procédé de refroidissement d'un rotor
DE102009024679B4 (de) * 2009-06-12 2016-04-07 Man Diesel & Turbo Se Verdichterlaufrad und damit ausgerüsteter Radialverdichter
DE102009034962B3 (de) * 2009-07-28 2011-01-13 Man Diesel & Turbo Se Radialverdichter
US9228497B2 (en) * 2010-12-30 2016-01-05 Rolls-Royce Corporation Gas turbine engine with secondary air flow circuit
JP5637899B2 (ja) * 2011-02-25 2014-12-10 株式会社Ｉｈｉ回転機械 膨張タービンの遮断板

Non-Patent Citations (1)

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Title
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Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN109209520A (zh) * 2018-09-13 2019-01-15 中国科学院工程热物理研究所 一种向心涡轮背部空腔泄漏流损失抑制密封技术

Also Published As

Publication number Publication date
DE102013203455A1 (de) 2014-08-28
JP5850965B2 (ja) 2016-02-03
JP2014169699A (ja) 2014-09-18
CN104018933B (zh) 2016-10-12
KR20140108123A (ko) 2014-09-05
EP2772652A3 (fr) 2018-03-28
CN104018933A (zh) 2014-09-03
KR101617938B1 (ko) 2016-05-18
EP2772652B1 (fr) 2021-10-06

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