EP0138480A2 - Zentrifugalkompressor - Google Patents

Zentrifugalkompressor Download PDF

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Publication number
EP0138480A2
EP0138480A2 EP19840306634 EP84306634A EP0138480A2 EP 0138480 A2 EP0138480 A2 EP 0138480A2 EP 19840306634 EP19840306634 EP 19840306634 EP 84306634 A EP84306634 A EP 84306634A EP 0138480 A2 EP0138480 A2 EP 0138480A2
Authority
EP
European Patent Office
Prior art keywords
diffuser
compressor
volute
impeller
neck
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.)
Withdrawn
Application number
EP19840306634
Other languages
English (en)
French (fr)
Inventor
Daniel A. Gutknecht
Richard Holtkamp
Dendall R. Swenson
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.)
Garrett Corp
Original Assignee
Garrett Corp
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 Garrett Corp filed Critical Garrett Corp
Publication of EP0138480A2 publication Critical patent/EP0138480A2/de
Withdrawn legal-status Critical Current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
    • 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

Definitions

  • This invention relates to a compressor and in particular to a compressor housing, for example, for use in conjunction with turbomachinery having a rotor adapted to operate at exceedingly high blade tip speeds.
  • turbomachinery as a fluid handling device is susceptible to noise generation as a result of high fluid velocities through and about fixed and moving blades, vanes, and channels.
  • Localised pressure fields resulting from the interaction between the fluid and the fluid handling structures result in the generation of regular cyclical pressure waves which cause noise.
  • Elimination and/or suppression of turbomachinery noise can be accomplished by redesigning the noise generating mechanism itself or by attenuating the effectiveness of the noise transmission mechanism.
  • the compressor is preferably a centrifugal compressor.
  • a centrifugal compressor In a radial outflow centrifugal compressor with or without a vaned diffuser, the geometry of the housing leads to the formation of an asymmetrical pressure field around the compressor wheel. As the compressor wheel blades pass through regions of higher and lower pressure, pressure impulses travel along the blade and cause noise. Furthermore, reduction of the circumferential pressure gradient will result in a reduction in the amplitude of the pressure pulse generated by the rotating wheel.
  • Turbomachinery may include a radial outflow centrifugal compressor with a vaned diffuser located radially outward from the compressor impeller.
  • the compressor impeller imparts energy to the air by increasing the velocity or kinetic energy of the air.
  • a channel of carefully controlled geometry wherein the air is diffused or slowed down in order to convert the dynamic pressure to static head pressure.
  • the diffuser through-the design of the vanes, serves to guide the flow from the impeller through channels between the vanes of increasing flow cross sectional area to provide optimal pressure recovery. Diffusion results in an increase in pressure and fluid density in the region around the diffuser plate.
  • the compressor housing design serves several purposes; it guides the air into the compressor impeller through its inlet, it shrouds the impeller and prevents leakage around the blades, it forms a sidewall for the diffuser and it collects the flow from the diffuser and channels it through its volute and discharges through the compressor outlet.
  • the geometry of the construction of the housing results in the formation of an asymmetrical field around the compressor impeller which assists in the undesirable generation of noise as discussed above.
  • one of the compressor housing's functions is to collect flow from the diffuser and deliver it to the inlet manifold of the engine.
  • the design features pertinent to this function have been determined to be a major cause of noise.
  • Such compressor housings may have a divider located at the point where the volute overlaps itself and which diverts the flow from the diffuser either to the compressor outlet or around the volute inside the compressor housing and thereafter through the compressor housing outlet.
  • the divider causes almost total stagnation of the fluid striking it and that creates a localized region of high static pressure. This non-uniform pressure distribution occurring in the compressor housing generates a circumferentially asymmetrical pressure field causing noise.
  • the present invention contemplates a compressor housing with revised geometry which minimizes the magnitude of the asymmetrical circumferential pressure gradient. More particularly, the present invention encompasses a design in which a divider neck or tongue extends to within close proximity of a region adjacent the compressor outlet where the fluid energy is substantially kinetic energy. For example, it may extend to one of the diffuser vanes thereby substantially eliminating the projection in the flow path and the region of high pressure stagnant air which is present in the existing designs.
  • the divider can extend to the diffuser inlet adjacent the compressor wheel outlet.
  • a compressor housing which may be used in a turbocharger of an internal combustion engine is composed of a volute section 12 and an integral shroud and diffuser plate section 14 having a shroud 16 and a diffuser plate 20.
  • the volute section 12 defines a volute 13 having an increasing cross-sectional area.
  • the end having the greatest cross-sectional area defines a compressor outlet 38 having its axis geneally tangential to the volute 13.
  • the shroud portion 16 is generally cylindrical on the outside with a venturi shaped cental opening therein.
  • the convergent portion of the venturi defines a compressor inlet 18.
  • the divergent portion expands radially outwards into the diffuser plate section 20.
  • a backplate 22 (not shown in FIGURES 2,5, or 7) separates the compressor housing 10 from the centre housing (not shown) of the turbocharger.
  • the backplate and the diffuser plate 20 defines between them an annular diffuser passage.
  • a compressor impeller 26 which is mounted on a drive shaft 28 for rotation by a prime mover (not shown), has a hub 30 of generally disc-shaped configuration with a plurality of circumferentially spaced blades 32 projecting from the hub 30 generally radially.
  • the blades 32 provide passages through which fluid flows by centrifugal force in response to the rotation of the impeller 26 to discharge radially about the compressor impeller; additional air flows axially through the compressor inlet 18 into the passages at the centre of the wheel to replace the air discharged.
  • the blades 32 are suitably curved to enhance the flow of the air into the passages.
  • shroud 16 is provided adjacent the outer edges of the blades 32 to confine the fluid in the passages formed thereby.
  • the diffuser element or plate 20 is provided around the periphery of the impeller 26.
  • the plate 20 consists of a circular plate and with a plurality of vanes 34 extending axially from one side of the plate. Vanes 34 are spaced radially from the centre and extend to the circumference of the plate 20 and are generally tangential to the periphery of the compressor impeller 26. Adjacent vanes, together with the diffuser plate 20 and a backplate 22 break up the annular diffuser passage 24 into a plurality of diffuser vane passages 36.
  • the diffuser vane passages 36 receive the fluid discharged at high velocity from the impeller and convert the velocity - (kinetic energy) - into the pressure - (static energy).
  • the housing volute 13 surrounding the periphery of the diffuser vane passages receives the fluid under pressure.
  • the diffuser passage 24 is annular in shape and is bounded axially by the diffuser plate 20 and backplate 22.
  • the volute section 12 defines a scroll-shaped air discharge chamber or volute 13 which extends at least 360° around the compressor inlet 18 and is in spaced relation thereto. Hence, at least a portion of the volute section 12 overlaps itself and therefore a portion of the larger end of the volute is in flow communication with the smaller end of the volute via an overlapping passage 44 ( shown in FIGURES 2 and 4).
  • the volute section 12 has a wall 15 which extends from the compressor outlet around to a dividing neck 40 which extends into the overlapping passage 44. Airflow from the smaller end of the volute can be discharged directly into the larger end of the volute through the overlapping passage 44 without travelling around the volute 13 and out the compressor outlet 38.
  • the overlapping passage 44 therefore creates a second flowpath for air leaving the diffuser passage 24 near the dividing neck 40.
  • ambient air enters axially through the compressor inlet 18, is compressed by the rotating compressor impeller 26 and flows radially through the diffuser passage 24 and into the compressor housing volute 13 before exiting through the compressor outlet 38 for communication to the inlet manifold of the engine.
  • FIGURES 1-4 the greatest resistance to flow has been found to exist in the area where air exits the diffuser passage 24 near the dividing neck 40; i.e. where flow can either enter the volute nearest to the compressor housing outlet 38 (the larger end of the volute) or flow into the volute 13 at its smaller end. This resistance creates a zone A of stagnant high pressure which, along with the rotating impeller causes noise as discussed above.
  • FIGURE 5 shows a fragmented side view of the compressor housing 10 including the outlet 38.
  • An extension 42 of the dividing neck 40 extends into the throat of the volute 13 such that its leading edge lies on the periphery of, or is connected to, the diffuser plate 20.
  • This extension 42 of the dividing neck 40 guides flow within the volute 13 such that flow through diffuser vane passage 36A must flow into the volute 13 at its smallest cross-section and counterclockwise as viewed in FIGURE 5. Flow from the adjacent diffuser vane passage 36B must exit straight to the compressor outlet 38.
  • Air flowing from either passage 36A or 36B does so without encountering the resistance to its flow experienced with the compressor housing design of FIGURE 2.
  • the air flow through diffuser vane passages 36A or 36B does not strike the neck 40, but is guided to flow on either side of it, and this eliminates the high pressure region of stagnant air (show as zone A in FIGURE 2), and thus eliminates a cause of turbocharger noise.
  • the dividing neck extension 42 extends into the volute 13 and together with one of the diffuser vanes 34A co-operates to eliminate any direct passage of air flow from diffuser vane passage 36A into the larger end of volute 13 immediately upstream of the compressor outlet 38.
  • the dividing neck extension 42 has been cross hatched in FIGURE 6 in order to show its shape clearly.
  • FIGURE 4 shows the air passage connecting the volute at its smallest end and the volute immediately upstream of the compressor outlet in a prior proposal.
  • the extension 42 is integral with the wall of the volute section 12. It is evident that the extension 42 has extended the wall 15 of the volute section 12 from the compressor outlet 38 to the periphery of the diffuser 20, and, with the diffuser vane 34A effectively to the periphery of the impeller 26.
  • zone A in FIGURE 2 the concept of eliminating the stagnant, high pressure zone can be accomplished in a vaneless compressor. This is done by extending the dividing neck 40 radially inward to a point at the periphery of the compressor impeller 26 as shown at 42 in FIGURE 7. This design is most feasible in the case where the diffuser plate 20 and the dividing neck 40 and its extension 42 are cast as an integral part of the housing.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
  • Supercharger (AREA)
EP19840306634 1983-10-03 1984-09-28 Zentrifugalkompressor Withdrawn EP0138480A2 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
US53826083A 1983-10-03 1983-10-03
US538260 1983-10-03

Publications (1)

Publication Number Publication Date
EP0138480A2 true EP0138480A2 (de) 1985-04-24

Family

ID=24146156

Family Applications (1)

Application Number Title Priority Date Filing Date
EP19840306634 Withdrawn EP0138480A2 (de) 1983-10-03 1984-09-28 Zentrifugalkompressor

Country Status (2)

Country Link
EP (1) EP0138480A2 (de)
JP (1) JPS6081498A (de)

Cited By (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN102562660A (zh) * 2012-02-07 2012-07-11 天津大学 离心通风机
US8545177B2 (en) 2007-07-23 2013-10-01 Continental Automotive Gmbh Radial compressor with a diffuser for use in a turbocharger
WO2015048231A1 (en) * 2013-09-30 2015-04-02 Borgwarner Inc. Controlling turbocharger compressor choke
EP2918790A1 (de) * 2014-03-12 2015-09-16 Mitsubishi Turbocharger and Engine Europe B.V. Verdichtergehäuse
CN106015096A (zh) * 2016-07-18 2016-10-12 湖南天雁机械有限责任公司 分体式涡轮增压器压气机蜗壳
US9574562B2 (en) 2013-08-07 2017-02-21 General Electric Company System and apparatus for pumping a multiphase fluid
WO2019042795A1 (en) 2017-08-30 2019-03-07 Unilever N.V. COMPOSITION OF PERSONAL CARE
US10527059B2 (en) 2013-10-21 2020-01-07 Williams International Co., L.L.C. Turbomachine diffuser
US11078922B2 (en) 2015-10-29 2021-08-03 Mitsubishi Heavy Industries Engine & Turbocharger, Ltd. Scroll casing and centrifugal compressor
US11421695B2 (en) 2018-01-19 2022-08-23 Concepts Nrec, Llc Turbomachines with decoupled collectors
CN116241508A (zh) * 2023-05-12 2023-06-09 潍柴动力股份有限公司 压气机的出气管、压气机及发动机

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH07103878B2 (ja) * 1989-01-19 1995-11-08 株式会社荏原製作所 ポンプケーシング及びその製造方法
JP4492045B2 (ja) * 2003-06-13 2010-06-30 株式会社Ihi 遠心圧縮機
JP5369198B2 (ja) * 2012-01-05 2013-12-18 トヨタ自動車株式会社 コンプレッサハウジング
JP6388772B2 (ja) * 2014-02-25 2018-09-12 三菱重工業株式会社 遠心圧縮機およびディフューザ製造方法

Cited By (15)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US8545177B2 (en) 2007-07-23 2013-10-01 Continental Automotive Gmbh Radial compressor with a diffuser for use in a turbocharger
CN102562660B (zh) * 2012-02-07 2014-02-26 天津大学 离心通风机
CN102562660A (zh) * 2012-02-07 2012-07-11 天津大学 离心通风机
US9574562B2 (en) 2013-08-07 2017-02-21 General Electric Company System and apparatus for pumping a multiphase fluid
WO2015048231A1 (en) * 2013-09-30 2015-04-02 Borgwarner Inc. Controlling turbocharger compressor choke
US10480398B2 (en) 2013-09-30 2019-11-19 Borgwarner Inc. Controlling turbocharger compressor choke
US10527059B2 (en) 2013-10-21 2020-01-07 Williams International Co., L.L.C. Turbomachine diffuser
EP2918790A1 (de) * 2014-03-12 2015-09-16 Mitsubishi Turbocharger and Engine Europe B.V. Verdichtergehäuse
US11078922B2 (en) 2015-10-29 2021-08-03 Mitsubishi Heavy Industries Engine & Turbocharger, Ltd. Scroll casing and centrifugal compressor
CN106015096A (zh) * 2016-07-18 2016-10-12 湖南天雁机械有限责任公司 分体式涡轮增压器压气机蜗壳
WO2019042795A1 (en) 2017-08-30 2019-03-07 Unilever N.V. COMPOSITION OF PERSONAL CARE
US11421695B2 (en) 2018-01-19 2022-08-23 Concepts Nrec, Llc Turbomachines with decoupled collectors
US12215698B2 (en) 2018-01-19 2025-02-04 Concepts Nrec, Llc Methods of manufacturing turbomachines having decoupled collectors
CN116241508A (zh) * 2023-05-12 2023-06-09 潍柴动力股份有限公司 压气机的出气管、压气机及发动机
CN116241508B (zh) * 2023-05-12 2023-09-15 潍柴动力股份有限公司 压气机的出气管、压气机及发动机

Also Published As

Publication number Publication date
JPS6081498A (ja) 1985-05-09

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PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

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Inventor name: HOLTKAMP, RICHARD

Inventor name: GUTKNECHT, DANIEL A.

Inventor name: SWENSON, DENDALL R.