EP1233190B1 - Compresseur centrifuge - Google Patents

Compresseur centrifuge Download PDF

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Publication number
EP1233190B1
EP1233190B1 EP02003087A EP02003087A EP1233190B1 EP 1233190 B1 EP1233190 B1 EP 1233190B1 EP 02003087 A EP02003087 A EP 02003087A EP 02003087 A EP02003087 A EP 02003087A EP 1233190 B1 EP1233190 B1 EP 1233190B1
Authority
EP
European Patent Office
Prior art keywords
housing
compressor
spiral
radial direction
bearing 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.)
Expired - Lifetime
Application number
EP02003087A
Other languages
German (de)
English (en)
Other versions
EP1233190A1 (fr
Inventor
Dr. Klaus Bartholomä
Wolfgang Schmidt
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.)
MAN Energy Solutions SE
Original Assignee
MAN Diesel and Turbo SE
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
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First worldwide family litigation filed litigation Critical https://patents.darts-ip.com/?family=7674629&utm_source=google_patent&utm_medium=platform_link&utm_campaign=public_patent_search&patent=EP1233190(B1) "Global patent litigation dataset” by Darts-ip is licensed under a Creative Commons Attribution 4.0 International License.
Application filed by MAN Diesel and Turbo SE filed Critical MAN Diesel and Turbo SE
Publication of EP1233190A1 publication Critical patent/EP1233190A1/fr
Application granted granted Critical
Publication of EP1233190B1 publication Critical patent/EP1233190B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D1/00—Radial-flow pumps, e.g. centrifugal pumps; Helico-centrifugal pumps
    • 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
    • F04D29/40—Casings; Connections of working fluid
    • F04D29/42—Casings; Connections of working fluid for radial or helico-centrifugal pumps
    • F04D29/4206—Casings; Connections of working fluid for radial or helico-centrifugal pumps 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
    • F01D25/00—Component parts, details, or accessories, not provided for in, or of interest apart from, other groups
    • F01D25/24—Casings; Casing parts, e.g. diaphragms, casing fastenings
    • 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
    • F01D9/00—Stators
    • F01D9/02—Nozzles; Nozzle boxes; Stator blades; Guide conduits, e.g. individual nozzles
    • F01D9/026—Scrolls for radial machines or engines
    • 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
    • F04D29/60—Mounting; Assembling; Disassembling
    • F04D29/62—Mounting; Assembling; Disassembling of radial or helico-centrifugal pumps
    • F04D29/624—Mounting; Assembling; Disassembling of radial or helico-centrifugal pumps especially adapted for elastic fluid pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05B—INDEXING SCHEME RELATING TO WIND, SPRING, WEIGHT, INERTIA OR LIKE MOTORS, TO MACHINES OR ENGINES FOR LIQUIDS COVERED BY SUBCLASSES F03B, F03D AND F03G
    • F05B2250/00—Geometry
    • F05B2250/10—Geometry two-dimensional
    • F05B2250/15—Geometry two-dimensional spiral
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05B—INDEXING SCHEME RELATING TO WIND, SPRING, WEIGHT, INERTIA OR LIKE MOTORS, TO MACHINES OR ENGINES FOR LIQUIDS COVERED BY SUBCLASSES F03B, F03D AND F03G
    • F05B2250/00—Geometry
    • F05B2250/20—Geometry three-dimensional
    • F05B2250/25—Geometry three-dimensional helical
    • 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

Definitions

  • the invention relates to a centrifugal compressor with a compressor wheel, which is enclosed by a spiral compressor housing with a helical flow channel, according to the preamble of patent claim 1.
  • Smaller turbochargers can absorb these forces due to the relatively large wall thicknesses and the rigid housing parts.
  • the housing wall thicknesses are usually reduced for casting reasons, whereby at such stress, the breaking point of the material is reached quickly and it can lead to housing breaks. It may leak fragments from the turbocharger, with considerable consequential damage.
  • the compressor housing an outer spiral housing, which comprises the radially outwardly deflected in the channel portion of the flow channel, and an inner Genosusprin lake which is provided in the radial direction between the volute casing and the compressor wheel and its inner contour with the outer contour of the hub of the compressor wheel the substantially extending in the axial direction channel portion of the flow channel, has, the spiral housing is designed with a housing insert at least partially surrounding inner cylinder to which the Genosusschreibrios is grown to form a cavity by means of a flexible fixation in the axial direction, and the flexible fixation of the Housing insert less unbreakable than the rigid fixation of the compressor housing is carried out on the bearing housing, a spiral housing has been formed with a "crumple zone" from this no fragment of a ruptured L. alsrades can escape more. The kinetic energy of fragments of a bursting compressor wheel can now be fully converted into deformation energy and heat within the turbocharger.
  • An additional burst protection outside the spiral housing can be omitted.
  • volute casing is designed with an inner cylinder at least partially surrounding the inner cylinder, on which the Gepatiusprin committee is grown to form a cavity by means of a flexible fixation in the axial direction, high protection against destruction of the volute casing itself is ensured and an effective "brake” given against leakage of debris from the turbocharger.
  • the intended for rigid fixation of the volute casing wall of the bearing housing in the radial direction is arranged pulled down over the outer tip of the outer contour of the compressor wheel to form a gap, so that an additional "brake”, ie securing against a radial escape of Fragments of the compressor wheel is specified.
  • a further particularly advantageous embodiment is the fact that the compressor housing is attached to the bearing housing via the outer spiral housing so as to form a parting line that the outer, the deflected channel section comprising volute to the rigid fixation of the compressor housing on the bearing housing over in the radial direction B to is pulled inside, so that the rigid fixation in the radial direction B is further outwardly disposed as the parting line between spiral and bearing housing.
  • This measure of the special arrangement of the parting line ensures that the rigid fixation of the compressor housing on the bearing housing is hardly burdened by any wedged in the flow channel fragments, whereby a breaking away of the compressor housing is further excluded.
  • the exhaust gas turbocharger of the type underlying in the drawing has a mounted in its central longitudinal region in a bearing housing shaft 1 2, which carries a not shown here turbine wheel and a schematically shown in the drawing radially flowed compressor wheel 3 at their projecting over the bearing ends.
  • the illustrated compressor wheel 3 has a hub 4 which is rotationally received on the shaft 2 driven by the turbine wheel and which is circumferentially occupied by radially projecting blades 5.
  • the outer contour 6 of the hub 4 bounded with the inner contour 7 of a compressor housing 8 a deflected from the axial direction A in the radial direction B, outwardly narrowing flow channel 9, whose cross section corresponds to the configuration of the blades 5.
  • the compressor housing 8 is fixed by means of a rigid fixation 18 on the bearing housing 1.
  • the diameter of the hub 4 and the blades 5 increases from the flow inlet to the flow outlet, so that a symmetrical to the median transverse plane of the compressor 3 longitudinal cross-section and, accordingly, over the length of the compressor 3 increasing mass distribution arise.
  • the compressor housing 8 is made of an outer fixed to the bearing housing by means of the rigid fixation 18 spiral housing 10, which comprises the outwardly deflected in the radial direction B channel portion 11 of the flow channel 9, and an inner Gepatiusprin Federation 12, in the radial direction B between the volute 10th and the compressor wheel 3 is provided and its inner contour 13 with the outer contour 6 of the hub 4 of the compressor wheel third forms the substantially extending in the axial direction A channel portion 14 of the flow channel 9, constructed.
  • the compressor housing 8 is attached via the outer volute casing 10 so as to form a parting line 22 on the bearing housing 1, that the outer, the deflected channel section 11 comprehensive volute 10 to the rigid fixation 18 of the compressor housing 8 on the bearing housing 1 over in the radial direction B inward is pulled, so that the rigid fixation 18 in the radial direction B further outwardly lying as the parting line 22 between the spiral-10 and bearing housing 1 is arranged.
  • This measure of the special arrangement of the parting line 22 ensures that the rigid fixation 18 of the compressor housing 8 on the bearing housing 1 is hardly burdened by any wedged in the flow channel 9 fragments, whereby a breaking away of the compressor housing 8 is further excluded.
  • the distance between the parting line 22 and the shaft 2 is smaller than the distance of the surface center 23 of the largest cross-sectional area 24 by the deflected channel portion 11 in the volute 10 to the shaft second
  • the spiral housing 10 is designed with an inner cylinder 15 at least partially surrounding the housing insert piece 12, on which the housing insert piece 12 is mounted to form a cavity 16 by means of a flexible fixing 17 in the axial direction A.
  • the flexible fixing 17 of the housing insert 12 is significantly less unbreakable than the rigid fixation 18 of the spiral housing 10 on the bearing housing 1 executed.
  • the rigid fixation 18 of the compressor housing 8, or the spiral housing 10 is by means of a fixed flange of the volute casing 10 on the bearing housing 1 and the flexible fixing 17 of the housing insert 12 by means of a Dehnschraubenfix ist in the axial direction A performed by the inner cylinder 15 of the spiral housing 10.
  • the intended for rigid fixation 18 of the volute 8 wall 19 of the bearing housing 1 is arranged in the radial direction B pulled down over the outer tip 20 of the outer contour 6 of the hub 4 of the compressor wheel 3 to form a gap 21.
  • the spiral housing 10 is designed with the diameter of the flow channel 9 becoming smaller and smaller towards the inside in the direction of the compressor wheel 3.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
  • Supercharger (AREA)

Claims (5)

  1. Compresseur centrifuge comportant une roue de compresseur (3) montée sur un arbre (2) logé dans le boîtier de palier (1) du compresseur centrifuge et dans le carter de compresseur (8),
    le contour extérieur (6) du moyeu (4) de la roue de compresseur (3) et le contour intérieur (7) du carter de compresseur (8) formant un canal d'écoulement (9) dévié de la direction axiale dans la direction radiale, et
    le carter de compresseur (8) est bloqué sur le boîtier de palier (1) par un moyen de fixation rigide (18),
    le carter de compresseur (8) est formé d'un carter en spirale (10), extérieur, comprenant le segment (11) du canal (9) dévié vers l'extérieur dans la direction radiale (B) et d'un insert de carter (12), intérieur, entre le carter en spirale (10) et le rotor de compresseur (3) dont le carter intérieur (13), forme avec le carter extérieur (6) du moyeu (4) du rotor de compresseur (3), le segment (14) de canal (9) pratiquement dirigé dans la direction axiale (A),
    caractérisé en ce que
    le carter en spirale (10) est formé d'un cylindre intérieur (15) entourant au moins en partie l'insert de carter (12), et auquel est assemblé l'insert de carter (12) pour former une cavité (16), à l'aide d'une fixation (17) souple dans la direction axiale (A), qui sort par une fixation à vis dilatable dans la direction axiale (A) du cylindre intérieur (15) du carter en spirale (10), pour être moins solide à la rupture que la fixation rigide (18) du carter de compresseur (8) sur le boîtier de palier (1).
  2. Compresseur centrifuge selon la revendication 1,
    caractérisé en ce que
    la fixation (18) rigide du carter de compresseur (8) est réalisée par une liaison par bride solide du carter en spirale (10) au boîtier de palier (1).
  3. Compresseur centrifuge selon la revendication 1,
    caractérisé en ce que
    la paroi (19) du boîtier de palier (1) prévue pour la fixation rigide (18) du carter en spirale (10), descend dans la direction radiale (B) jusqu'au-delà de l'autre pointe (20) du contour extérieur (6) du moyeu (4) de la roue de compresseur (3) en formant un intervalle (21).
  4. Compresseur centrifuge selon les revendications précédentes,
    caractérisé en ce que
    le carter de compresseur (8) est appliqué contre le boîtier de palier (1) par le carter en spirale (10) extérieur, en formant un joint d'assemblage (22) de façon que le carter en spirale (10), extérieur comprenant le segment de canal dévié (11), sur la fixation rigide (18) en étant tiré vers l'intérieur dans la direction radiale (B) de façon que dans la direction radiale (B), la fixation rigide (18) se trouve plus à l'extérieur que le joint d'assemblage (22) entre le carter en spirale (10) et le boîtier de palier (1).
  5. Compresseur centrifuge selon la revendication 4,
    caractérisé en ce que
    la distance entre le joint d'assemblage (22) et l'arbre (2) est inférieure à la distance entre le centre (23) de la plus grande surface de section (24) du segment de canal (11) dévié du carter en spirale (10) par rapport à l'arbre (2).
EP02003087A 2001-02-20 2002-02-13 Compresseur centrifuge Expired - Lifetime EP1233190B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE10107807 2001-02-20
DE10107807A DE10107807C1 (de) 2001-02-20 2001-02-20 Strömungsmaschine mit radial durchströmtem Verdichterrad

Publications (2)

Publication Number Publication Date
EP1233190A1 EP1233190A1 (fr) 2002-08-21
EP1233190B1 true EP1233190B1 (fr) 2010-06-02

Family

ID=7674629

Family Applications (1)

Application Number Title Priority Date Filing Date
EP02003087A Expired - Lifetime EP1233190B1 (fr) 2001-02-20 2002-02-13 Compresseur centrifuge

Country Status (6)

Country Link
US (1) US6638007B2 (fr)
EP (1) EP1233190B1 (fr)
JP (1) JP4119654B2 (fr)
KR (1) KR100794974B1 (fr)
CN (1) CN1267648C (fr)
DE (2) DE10107807C1 (fr)

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CN105065328B (zh) * 2015-08-06 2017-11-14 中国北方发动机研究所(天津) 一种用于离心压气机的双槽自动调节机匣处理装置

Also Published As

Publication number Publication date
KR100794974B1 (ko) 2008-01-15
CN1372082A (zh) 2002-10-02
US20020114693A1 (en) 2002-08-22
JP4119654B2 (ja) 2008-07-16
EP1233190A1 (fr) 2002-08-21
KR20020068271A (ko) 2002-08-27
DE10107807C1 (de) 2002-07-25
DE50214459D1 (de) 2010-07-15
JP2002257092A (ja) 2002-09-11
CN1267648C (zh) 2006-08-02
US6638007B2 (en) 2003-10-28

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