WO2009071621A1 - Carter de compresseur - Google Patents

Carter de compresseur Download PDF

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Publication number
WO2009071621A1
WO2009071621A1 PCT/EP2008/066777 EP2008066777W WO2009071621A1 WO 2009071621 A1 WO2009071621 A1 WO 2009071621A1 EP 2008066777 W EP2008066777 W EP 2008066777W WO 2009071621 A1 WO2009071621 A1 WO 2009071621A1
Authority
WO
WIPO (PCT)
Prior art keywords
sectional area
cross
compressor
outlet housing
collecting space
Prior art date
Application number
PCT/EP2008/066777
Other languages
German (de)
English (en)
Inventor
Niklas Sievers
Hans-Peter Dickmann
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 WO2009071621A1 publication Critical patent/WO2009071621A1/fr

Links

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
    • 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
    • F04D29/44—Fluid-guiding means, e.g. diffusers
    • F04D29/441—Fluid-guiding means, e.g. diffusers especially adapted for elastic fluid pumps

Definitions

  • the invention relates to the field of centrifugal compressors, as used for example in exhaust gas turbochargers for charging internal combustion engines.
  • the invention relates to an outlet housing of such a radial compressor.
  • Radial compressors are used, for example, in the exhaust gas turbocharger or as an industrial compressor in the process industry.
  • Exhaust gas turbochargers are used to increase the performance of internal combustion engines (reciprocating engines).
  • An exhaust gas turbocharger consists of an exhaust gas turbine in the exhaust gas stream of the internal combustion engine and the compressor in the intake tract of the internal combustion engine.
  • the turbine wheel of the exhaust gas turbine is set in rotation by the exhaust gas flow of the engine and drives the impeller of the compressor via a shaft.
  • the compressor increases the pressure in the intake tract of the internal combustion engine, so that when sucking a larger amount of air enters the combustion chambers.
  • the air flows axially into the impeller of the compressor stage and is then deflected outwards, in the radial direction.
  • the volume flow exiting the compressor wheel, so that it can be supplied to the internal combustion engine, must be collected after the radial diffuser over the circumference.
  • spirals or collectors are used as collecting space. Spirals have an increasing cross-sectional area around the circumference, whereas collectors have a constant cross-sectional area around the circumference. In modern radial compressor stages with high demands on efficiency and pressure ratio spirals are usually used, since they have a lower loss coefficient compared to collectors.
  • the cross-sectional area increase is generally designed so that the volume flow is collected continuously and forms a homogeneous flow field over the circumference.
  • the volume flow flowing out of the radial diffuser is divided into a first partial flow, which is collected over the circumference and a second partial flow, which flows directly into the downstream diffuser.
  • the second partial flow the flow is raised upright, less strong in the first partial flow.
  • a measure for the assessment of the circumferential asymmetry is the normalized pressure or the normalized pressure difference, also called distortion.
  • the extent of the circumferential asymmetry depends on the spiral geometry and the diffuser blade number, the distance of the diffuser blade trailing edge to the spiral inlet, the diffuser type, the impeller or the volume flow, etc. The circumferential asymmetry can directly and indirectly lead to negative effects on the efficiency of the compressor stage.
  • the spiral surface is formed along the entire circumference of the spiral up to the beginning of the spiral.
  • the tongue can be modified.
  • the spiral surface is not formed in the area of the penetration, so that the spiral begins after penetration (this is referred to as a "cut-out tongue").
  • asymmetrically designed radial diffusers can also be used.
  • their production is complex and expensive.
  • the object of the present invention is to modify an outlet housing for a radial compressor such that the circumferential asymmetry and the resulting pressure variation are significantly reduced.
  • This can be achieved by modifying the cross-sectional area of the collecting space in the outlet housing according to the invention.
  • a certain cross-sectional area is selected, for example, the cross-sectional area at 120 °.
  • this cross-sectional area replaces the original cross-sectional areas between the beginning of the spiral and this cross-sectional area, so that the collecting space has a constant, smallest cross-sectional area over the first 120 °. The rest of the collection space remains unchanged as a spiral.
  • the collection space has a constant area and an area with increasing cross-sectional area, so represents a combination of a collector - on the first 120 ° - and a spiral.
  • the tongue design - cut / not cut - there is an optional modification in the diffuser area , wherein the diffuser cross-sectional area remains unchanged in both cases.
  • Fig. 1 shows a first embodiment of an inventively designed compressor outlet housing with a collecting space portion with a constant
  • FIG. 2 shows the course of the cross-sectional area of the collecting space according to FIG. 1, FIG.
  • FIG. 3 shows a second embodiment of a compressor outlet housing designed according to the invention with two collecting chamber sections, each with a constant cross-sectional area,
  • FIG. 4 shows the course of the cross-sectional area of the collecting space according to FIG. 2, FIG.
  • FIG. 5 shows a guided along V-V section through the compressor outlet housing according to Fig. 1, and
  • FIG. 6 shows a diagram with the course of the normalized pressure over the circumferential angle for a conventional compressor outlet housing and a compressor outlet housing according to FIG. 1 configured according to the invention.
  • Fig. 1 shows a first embodiment of a modified outlet housing 1 of a centrifugal compressor.
  • the outlet housing has two openings.
  • the first opening is annular and open radially against the inside. Through this opening, the air coming from the compressor wheel and the radial diffuser 42 flows into the collecting space, which is designated in FIG. 1 with coarse hatching.
  • the radial diffuser extends between the compressor wheel and the collecting space in the outlet housing. It can optionally be limited by separate components and / or equipped with diffuser blades.
  • the second opening is located in the outlet flange 12, at the end of the collecting space and the subsequent thereto diffuser 30, which is designated in Fig. 1 with fine hatching. Through the second opening, the air is discharged to the engine.
  • Fig. 5 shows a guided along VV Section through this area of the outlet housing.
  • the tongue can optionally be omitted, as described above.
  • the portion 21 of the collecting space and the diffuser 30 in the initial region of the spiral winding are not delimited by any housing part.
  • the air exiting the compressor wheel and the adjacent radial diffuser 42 with the guide vanes 41 is indicated in FIG. 1 by the curved arrows.
  • the cross-sectional area increases, as is usual for a spiral.
  • the designated cross-sectional area Ai 8 o is already greater than the cross-sectional area Ai 20 at the end of the first section 21.
  • the course of a conventional spiral in the first section 21 is indicated by a thin line.
  • the cross-sectional area of the plenum of the first embodiment is shown schematically in FIG. In section 21, between 0 ° and 120 °, the cross-sectional area is constant, and in section 22, from 120 ° to 360 °, the cross-sectional area increases continuously.
  • FIG. 3 shows a second embodiment of a modified outlet housing 1 of a centrifugal compressor.
  • the collection room is divided into four sections.
  • the cross-sectional area increases, as is usual for a spiral.
  • the designated cross-sectional area Ai 80 at the end of the second section 22 is greater than the cross-sectional area Ai 20 at the end of the first section 21.
  • the cross-sectional area increases again, as is usual for a spiral.
  • the unspecified cross-sectional area at the end of the fourth section 24 is greater than the cross-sectional area A 24 o at the end of the third section 23.
  • the cross-sectional area of the plenum of the second embodiment is shown schematically in FIG. In section 21, between 0 ° and 120 ° and in section 23, between 180 ° and 240 °, the cross-sectional area is constant, in section 22, from 120 ° to 180 °, and in section 24, from 240 ° to 360 ° , the cross-sectional area increases continuously.
  • the specified circumferential angle values for the limitation of the individual sections, in particular in the first embodiment, are the result of simulation calculations.
  • Fig. 6 shows in comparison with a conventional spiral (solid line) the course of the normalized pressure in an outlet housing according to the first embodiment.
  • the result is a distortion reduced by up to 30%, which results in a more uniform flow around the blades of the radial diffuser, resulting in increased efficiency.
  • the backflow of air from the diffuser into the collecting space can be significantly reduced, whereby a more continuous collecting of the volume flow takes place.
  • the low-impulse region directly after the tongue, in which the back-flowing air collects is greatly reduced. Together with the larger cross-sectional area results in a Entdrosselung and consequently a higher throughput of the compressor stage.
  • the two-dimensional configuration of the cross section may vary along the circumference of the plenum. LIST OF REFERENCES Outlet housing outlet flange of the outlet housing tongue, 23 plenum section with constant cross-sectional area, 24 plenum section with increasing cross-sectional area of the diffuser radial diffuser radial diffuser

Landscapes

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

Abstract

L'invention vise à réduire l'asymétrie périphérique dans des carters de refoulement de compresseurs. À cet effet, un espace de collecte comprend deux parties (21, 22) présentant chacune une aire de section de configuration différente, ce qui permet d'améliorer l'écoulement à travers les composants montés en amont, à savoir le diffuseur radial et le rotor, et d'obtenir une collecte plus homogène du débit volumique sur la périphérie et ainsi un rendement accru.
PCT/EP2008/066777 2007-12-07 2008-12-04 Carter de compresseur WO2009071621A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
EP07122647.6 2007-12-07
EP07122647A EP2068002A1 (fr) 2007-12-07 2007-12-07 Boîtier de compresseur

Publications (1)

Publication Number Publication Date
WO2009071621A1 true WO2009071621A1 (fr) 2009-06-11

Family

ID=39386152

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP2008/066777 WO2009071621A1 (fr) 2007-12-07 2008-12-04 Carter de compresseur

Country Status (2)

Country Link
EP (1) EP2068002A1 (fr)
WO (1) WO2009071621A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2019097730A1 (fr) * 2017-11-20 2019-05-23 三菱重工エンジン＆ターボチャージャ株式会社 Compresseur centrifuge et turbocompresseur pourvu dudit compresseur

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CH286975A (de) * 1951-05-01 1952-11-15 Karrer Josef Fliehkraftgebläse, insbesondere Ventilator mit Spiralgehäuse.
WO1990009524A1 (fr) * 1989-02-14 1990-08-23 Airflow Research & Manufacturing Corporation Ventilateur centrifuge et diffuseur a volute d'accumulation
EP0570955A1 (fr) * 1992-05-20 1993-11-24 Praxair Technology, Inc. Collecteur d'un compresseur à section transversale non-uniforme
WO2001000996A1 (fr) * 1999-06-30 2001-01-04 Alliedsignal Inc. Carter de compresseur moule sous pression, destine aux compresseurs centrifuges et presentant une vraie forme de volute
WO2007033199A2 (fr) * 2005-09-13 2007-03-22 Ingersoll-Rand Company Volute destinee a s'utiliser avec un compresseur centrifuge

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CH286975A (de) * 1951-05-01 1952-11-15 Karrer Josef Fliehkraftgebläse, insbesondere Ventilator mit Spiralgehäuse.
WO1990009524A1 (fr) * 1989-02-14 1990-08-23 Airflow Research & Manufacturing Corporation Ventilateur centrifuge et diffuseur a volute d'accumulation
EP0570955A1 (fr) * 1992-05-20 1993-11-24 Praxair Technology, Inc. Collecteur d'un compresseur à section transversale non-uniforme
WO2001000996A1 (fr) * 1999-06-30 2001-01-04 Alliedsignal Inc. Carter de compresseur moule sous pression, destine aux compresseurs centrifuges et presentant une vraie forme de volute
WO2007033199A2 (fr) * 2005-09-13 2007-03-22 Ingersoll-Rand Company Volute destinee a s'utiliser avec un compresseur centrifuge

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2019097730A1 (fr) * 2017-11-20 2019-05-23 三菱重工エンジン＆ターボチャージャ株式会社 Compresseur centrifuge et turbocompresseur pourvu dudit compresseur
JPWO2019097730A1 (ja) * 2017-11-20 2020-04-16 三菱重工エンジン＆ターボチャージャ株式会社 遠心圧縮機及びこの遠心圧縮機を備えたターボチャージャ
US11060529B2 (en) 2017-11-20 2021-07-13 Mitsubishi Heavy Industries Engine & Turbocharger, Ltd. Centrifugal compressor and turbocharger including the same

Also Published As

Publication number Publication date
EP2068002A1 (fr) 2009-06-10

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