EP2181268B1 - Compresseur radial doté d'un distributeur et destiné à un turbocompresseur - Google Patents

Compresseur radial doté d'un distributeur et destiné à un turbocompresseur Download PDF

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Publication number
EP2181268B1
EP2181268B1 EP08785006.1A EP08785006A EP2181268B1 EP 2181268 B1 EP2181268 B1 EP 2181268B1 EP 08785006 A EP08785006 A EP 08785006A EP 2181268 B1 EP2181268 B1 EP 2181268B1
Authority
EP
European Patent Office
Prior art keywords
diffuser
region
compressor
radial compressor
tongue
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.)
Not-in-force
Application number
EP08785006.1A
Other languages
German (de)
English (en)
Other versions
EP2181268A1 (fr
Inventor
Tobias Dettmann
Andre Kaufmann
Stefan Krauss
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.)
Continental Automotive GmbH
Original Assignee
Continental Automotive GmbH
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 Continental Automotive GmbH filed Critical Continental Automotive GmbH
Publication of EP2181268A1 publication Critical patent/EP2181268A1/fr
Application granted granted Critical
Publication of EP2181268B1 publication Critical patent/EP2181268B1/fr
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

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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
    • 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
    • F04D29/444—Bladed diffusers
    • 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
    • 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
    • F04D29/422—Discharge tongues
    • 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
    • F05D2250/00—Geometry
    • F05D2250/50—Inlet or outlet
    • F05D2250/52—Outlet

Definitions

  • the invention relates to a centrifugal compressor with a diffuser which is used for example in an exhaust gas turbocharger for a motor vehicle.
  • Turbochargers generally consist of an exhaust gas turbine in an exhaust gas flow, which is connected via a turbo shaft with a compressor in the intake tract.
  • a turbine wheel and a compressor wheel are rotatably mounted on the turbo shaft, wherein the turbine wheel is arranged in a turbine housing and the compressor wheel in a compressor housing with a diffuser.
  • the exhaust gas flow passing through the turbine housing drives the turbine wheel.
  • the turbine wheel in turn drives the compressor wheel, causing the compressor to increase the pressure in the intake tract of the engine, so that a larger amount of air enters the cylinder during the intake stroke. This means that more oxygen is available and a correspondingly larger amount of fuel can be burned. As a result, the power output of the engine can be increased.
  • the compressor Decisive for the noise emission of the turbocharger here is the compressor.
  • the compressor discharge radiates a lot of noise to the outside.
  • Radial compressors for exhaust gas turbochargers are known from the prior art, which have a diffuser, which converts the built-up speed in pressure.
  • a diffuser ends in a so-called spiral which discharges the compressed air to the consumer.
  • the geometry of the transition of the spiral, ie the so-called tongue, is in this case a critical embodiment element, since pressure pulsations often arise at this point.
  • the problem of the formation of such pressure pulsations has hitherto been fluidic favorable shape of the tongue with a constant diffuser diameter or radius solved.
  • Such a radial compressor is for example off US 2005/232762 A1 known.
  • a compressor housing that achieves a reduced weight and reduced number of parts with the task of maximizing performance while still withstanding the high operating stresses imposed by the pressure and external structural loadings.
  • an arrangement of guide vanes, which are formed integrated on the screw housing wall are proposed, on the one hand direct the flow of fluid and on the other hand support the housing stabilizing.
  • silencers are frequently used. These silencers may have channel-like or backdrop-like elements, which in turn are lined, for example, with sound-absorbing material.
  • absorption mufflers it is also possible to use acoustic resonators and acoustic filters for soundproofing.
  • centrifugal compressor with a diffuser and a turbocharger with a centrifugal compressor designed in such a way are that the occurrence of pressure pulsations can at least be reduced or substantially prevented.
  • the diffuser in the region of the transition of the spiral housing ie in the region of the tongue has a larger or larger width and such an increased radius that it has a bulge in the manner of an oval, the formation of a negative pressure area is prevented or at least reduced , so that disturbing pulsations can be contained and thus the occurrence of corresponding noise.
  • the radial compressor has the advantage that disturbing pressure pulsations can be prevented by reducing or suppressing a negative pressure area, which arises above all in the region of the transition of the spiral housing in the diffuser.
  • the use of additional silencers at least partially or completely be waived. This results in a significant saving in terms of manufacturing and assembly costs.
  • a more compact design can be achieved, for example, when used in a turbocharger.
  • This has the further advantage that the cross-section of a diffuser can be relatively easily adapted or changed and is therefore less expensive and requires no additional space compared to the use of mufflers in the prior art.
  • the cross section of the diffuser is varied by increasing the width and the radius or the diameter of the diffuser in the region of the transition of the spiral housing, ie in the region of the tongue.
  • At least one wall or both opposing walls of the diffuser are outwardly inclined and / or arched.
  • the respective wall can form a wedge shape, whereby the wedge shape increases towards the outside.
  • the walls can be identical or different in shape, inclination and / or curvature. This has the advantage that, depending on the function and intended use, the width of the diffuser can be easily achieved in at least one area by adapting both walls or even just one wall.
  • a radial compressor 10 is shown with a diffuser 12 according to the prior art, which is part of a turbocharger (not shown).
  • the radial compressor 10 is shown simplified from the front in a sectional view.
  • the radial compressor 10 in this case has a volute casing 14 and the diffuser 12.
  • the radius r1 or the diameter of the diffuser 12 is constant.
  • the width b1 of the diffuser 12 is constant as in the following Fig. 2 is shown.
  • the diffuser 12 therefore has a substantially constant cross section.
  • a turbo shaft 16 is arranged, on which a compressor wheel 18 is provided.
  • the compressor wheel 18 is driven via a corresponding turbine wheel (not shown) on the turbo shaft 16.
  • 18 air is sucked axially by the speed of the compressor wheel and accelerated in the compressor 18 to high speeds. The air leaves the compressor wheel 18 while in the radial direction.
  • the diffuser 12 In the diffuser 12, the velocity of the air is reduced. The consequence of this is that pressure and temperature increase.
  • the diffuser 12 is formed, for example, from a compressor rear wall and a part of the spiral housing 14. In the volute 14, the air is collected and the speed up to the compressor outlet further reduced. In this case, the geometry of the transition of the spiral 13 of the volute 14, ie the so-called. Tongue 20, forms a critical execution element, since at this point often pressure pulsations arise because here can form a negative pressure area.
  • mufflers (not shown) are provided to prevent or at least reduce disturbing noises as a result of such pressure pulsations.
  • Fig. 2 is a sectional view through the diffuser 12 and the compressor 18 according to Fig. 1 shown.
  • the width b1 of the diffuser 12 is kept substantially constant.
  • a radial compressor 10 is shown, which is part of a turbocharger (not shown).
  • the radial compressor 10 also has a volute casing 14 and a diffuser 12.
  • On a turbo shaft 16 is, as previously with reference to Fig. 1 a compressor wheel 18 and, for example, a turbine wheel (not shown).
  • the diffuser 12 converts the built-up speed of the air sucked in via the compressor wheel 18 into pressure.
  • the diffuser 12 terminates in the spiral 13 of the spiral housing 14, which discharges the compressed air to the consumer.
  • the cross section of the diffuser 12 is changed here.
  • the cross section of the diffuser 12 is varied and is therefore not constant, in contrast to the previously indicated prior art.
  • the radius r or the diameter of the diffuser 12 is designed or changed as follows.
  • the radius r or the diameter of the diffuser 12 is designed such that the formation of a negative pressure area is reduced or substantially no negative pressure area in the region of the tongue 20, ie in the region of the Transition of the spiral, arises. This is achieved, for example, by increasing the radius r or the diameter of the diffuser 12 in at least one predetermined area, in order to reduce or substantially prevent the formation of a negative pressure area.
  • a radius r2 of the diffuser is therefore chosen to be larger in the region of the tongue 20 than a radius r1 of the diffuser 12 outside this range.
  • the diffuser 12 as in Fig. 3 is shown, for example, in the region of the tongue 20 and the transition of the spiral 13 are carried out with a larger radius r2 or larger diameter.
  • the diffuser 12 is formed, for example, in the region of the tongue 20 with a curvature 30 to the outside or forms an oval in this area.
  • the representation in Fig. 3 is greatly simplified.
  • Fig. 4 is further a sectional view through the compressor wheel 18 and the diffuser 12 according to Fig. 3 shown.
  • the diffuser 12 has a substantially constant width b1.
  • FIG. 5 Now another embodiment of the radial compressor 10 is shown.
  • the radial compressor 10 has a constant diameter or radius r1.
  • the width b of the diffuser 12 is changed here.
  • the width b of the diffuser 12 is varied in at least one range in order to counteract the previously described pressure pulsations which occur, for example, in the region of the transition of the spiral 13.
  • the width b of the diffuser 12 is here, for example, increased, as in Fig. 6 is shown.
  • the width b1 is increased in the illustrated area to a width b2.
  • a first wall 22 of the diffuser 12 is formed in this area, for example, slightly inclined by an angle ⁇ outwards.
  • the first wall 22 can also be curved, for example.
  • an opposite second wall 24 of the diffuser 12 can be adjusted accordingly.
  • a diffuser 12 according to the invention additionally has a varied diameter or radius r in each of the at least one region, as described with reference to FIGS 3 and 4 previously described in detail.
  • the cross section of the diffuser 12 is varied over the width b and the diameter or radius r.
  • first and / or second wall 22, 24 of the diffuser 12 can be outwardly inclined and / or arched in order to increase the width b of the diffuser 12.
  • the two walls 22, 24 may be identical or differently shaped, i. for example, with different inclinations or vaults.
  • the walls 22, 24 may also have different shapes in this area.
  • one wall 22, 24 inclined and the other wall 22, 24 may be curved, depending on the function and purpose.

Landscapes

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

Claims (6)

  1. Compresseur radial (10), destiné en particulier à un turbocompresseur, comprenant :
    - un boîtier en spirale (14) et
    - un diffuseur (12), la section du diffuseur (12) dans la région de la transition du boîtier en spirale (14), donc dans la région de la languette (20), étant modifiée de manière à au moins réduire la formation d'une région de dépression dans cette région,
    caractérisé en ce que
    le diffuseur (12) a une largeur (b) relativement plus grande dans la région de la languette (20) et en ce que le rayon (r) du diffuseur (12) est augmenté dans la région de la languette (20) de manière à présenter un renflement (30) à la manière d'un ovale.
  2. Compresseur radial selon la revendication 1,
    caractérisé en ce que
    au moins une paroi (22, 24) ou les deux parois opposées (22, 24) du diffuseur (12) sont inclinées et/ou incurvées vers l'extérieur.
  3. Compresseur radial selon la revendication 2,
    caractérisé en ce que
    les parois (22, 24) ont des formes, des inclinaisons et/ou des incurvations identiques ou différentes.
  4. Compresseur radial selon l'une des revendications 2 ou 3,
    caractérisé en ce que
    la paroi respective (22, 24) a une forme de coin.
  5. Compresseur radial selon la revendication 4,
    caractérisé en ce que
    la forme de coin s'agrandit en direction de l'extérieur.
  6. Turbocompresseur à compresseur radial (10) selon l'une au moins des revendications 1 à 5.
EP08785006.1A 2007-07-23 2008-07-23 Compresseur radial doté d'un distributeur et destiné à un turbocompresseur Not-in-force EP2181268B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102007034236A DE102007034236A1 (de) 2007-07-23 2007-07-23 Radialverdichter mit einem Diffusor für den Einsatz bei einem Turbolader
PCT/EP2008/006053 WO2009012990A1 (fr) 2007-07-23 2008-07-23 Compresseur radial doté d'un distributeur et destiné à un turbocompresseur

Publications (2)

Publication Number Publication Date
EP2181268A1 EP2181268A1 (fr) 2010-05-05
EP2181268B1 true EP2181268B1 (fr) 2018-12-26

Family

ID=40091759

Family Applications (1)

Application Number Title Priority Date Filing Date
EP08785006.1A Not-in-force EP2181268B1 (fr) 2007-07-23 2008-07-23 Compresseur radial doté d'un distributeur et destiné à un turbocompresseur

Country Status (5)

Country Link
US (1) US8545177B2 (fr)
EP (1) EP2181268B1 (fr)
JP (1) JP5124636B2 (fr)
DE (1) DE102007034236A1 (fr)
WO (1) WO2009012990A1 (fr)

Families Citing this family (18)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP5479316B2 (ja) 2010-12-28 2014-04-23 三菱重工業株式会社 遠心圧縮機のスクロール構造
JP5517981B2 (ja) 2011-03-17 2014-06-11 三菱重工業株式会社 遠心圧縮機のスクロール構造
DE102011085118A1 (de) * 2011-10-24 2013-04-25 Robert Bosch Gmbh Halterung für elektrische Maschinen
JP5905268B2 (ja) * 2012-01-17 2016-04-20 三菱重工業株式会社 遠心圧縮機
US9915270B2 (en) 2013-02-01 2018-03-13 Borgwarner Inc. Turbocharger compressor with an elliptical diffuser wall
DE112014005001T5 (de) * 2013-10-31 2016-07-14 Ihi Corporation Zentrifugalkompressor und Turbolader
DE102014012765A1 (de) * 2014-09-02 2016-03-03 Man Diesel & Turbo Se Radialverdichterstufe
DE102014012764A1 (de) * 2014-09-02 2016-03-03 Man Diesel & Turbo Se Radialverdichterstufe
JP6470853B2 (ja) 2015-12-25 2019-02-13 三菱重工エンジン＆ターボチャージャ株式会社 遠心圧縮機及びターボチャージャ
CN109072940B (zh) 2016-07-01 2020-05-26 株式会社Ihi 离心压缩机
JP6642711B2 (ja) * 2016-07-01 2020-02-12 株式会社Ihi 遠心圧縮機
JP6842564B2 (ja) 2017-11-06 2021-03-17 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
DE102017127758A1 (de) * 2017-11-24 2019-05-29 Man Diesel & Turbo Se Radialverdichter und Turbolader
JP6768628B2 (ja) 2017-12-06 2020-10-14 三菱重工マリンマシナリ株式会社 遠心圧縮機及びターボチャージャ
US10935045B2 (en) * 2018-07-19 2021-03-02 GM Global Technology Operations LLC Centrifugal compressor with inclined diffuser
DE112019007061T5 (de) 2019-05-30 2021-12-16 Mitsubishi Heavy Industries Engine & Turbocharger, Ltd. Zentrifugalkompressor und turbolader
US11286952B2 (en) * 2020-07-14 2022-03-29 Rolls-Royce Corporation Diffusion system configured for use with centrifugal compressor
WO2023188246A1 (fr) * 2022-03-31 2023-10-05 三菱重工エンジン＆ターボチャージャ株式会社 Capot de compresseur, compresseur centrifuge, turbocompresseur, procédé de fabrication de capot de compresseur et diffuseur pour compresseur centrifuge

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Also Published As

Publication number Publication date
EP2181268A1 (fr) 2010-05-05
US20100178163A1 (en) 2010-07-15
JP2010529358A (ja) 2010-08-26
JP5124636B2 (ja) 2013-01-23
WO2009012990A1 (fr) 2009-01-29
DE102007034236A1 (de) 2009-02-05
US8545177B2 (en) 2013-10-01

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