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US20080008595A1 - Compressor wheel - Google Patents

Compressor wheel Download PDF

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Publication number
US20080008595A1
US20080008595A1 US11/803,206 US80320607A US2008008595A1 US 20080008595 A1 US20080008595 A1 US 20080008595A1 US 80320607 A US80320607 A US 80320607A US 2008008595 A1 US2008008595 A1 US 2008008595A1
Authority
US
United States
Prior art keywords
compressor wheel
backface
layer
compressive stress
residual compressive
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.)
Abandoned
Application number
US11/803,206
Other languages
English (en)
Inventor
David McKenzie
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.)
Cummins Turbo Technologies Ltd
Original Assignee
Cummins Turbo Technologies Ltd
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
Family has litigation
First worldwide family litigation filed litigation Critical https://patents.darts-ip.com/?family=33523680&utm_source=google_patent&utm_medium=platform_link&utm_campaign=public_patent_search&patent=US20080008595(A1) "Global patent litigation dataset” by Darts-ip is licensed under a Creative Commons Attribution 4.0 International License.
Application filed by Cummins Turbo Technologies Ltd filed Critical Cummins Turbo Technologies Ltd
Assigned to CUMMINS TURBO TECHNOLOGIES LIMITED reassignment CUMMINS TURBO TECHNOLOGIES LIMITED ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: MCKENZIE, DAVID
Publication of US20080008595A1 publication Critical patent/US20080008595A1/en
Priority to US12/731,741 priority Critical patent/US8641380B2/en
Abandoned 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
    • F04D29/26—Rotors specially for elastic fluids
    • F04D29/28—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps
    • C—CHEMISTRY; METALLURGY
    • C21—METALLURGY OF IRON
    • C21D—MODIFYING THE PHYSICAL STRUCTURE OF FERROUS METALS; GENERAL DEVICES FOR HEAT TREATMENT OF FERROUS OR NON-FERROUS METALS OR ALLOYS; MAKING METAL MALLEABLE, e.g. BY DECARBURISATION OR TEMPERING
    • C21D7/00—Modifying the physical properties of iron or steel by deformation
    • C21D7/02—Modifying the physical properties of iron or steel by deformation by cold working
    • C21D7/04—Modifying the physical properties of iron or steel by deformation by cold working of the surface
    • C—CHEMISTRY; METALLURGY
    • C21—METALLURGY OF IRON
    • C21D—MODIFYING THE PHYSICAL STRUCTURE OF FERROUS METALS; GENERAL DEVICES FOR HEAT TREATMENT OF FERROUS OR NON-FERROUS METALS OR ALLOYS; MAKING METAL MALLEABLE, e.g. BY DECARBURISATION OR TEMPERING
    • C21D7/00—Modifying the physical properties of iron or steel by deformation
    • C21D7/02—Modifying the physical properties of iron or steel by deformation by cold working
    • C21D7/04—Modifying the physical properties of iron or steel by deformation by cold working of the surface
    • C21D7/08—Modifying the physical properties of iron or steel by deformation by cold working of the surface by burnishing or the like
    • 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
    • F04D29/26—Rotors specially for elastic fluids
    • 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
    • F04D29/26—Rotors specially for elastic fluids
    • F04D29/266—Rotors specially for elastic fluids mounting compressor rotors on shafts
    • 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
    • F04D29/26—Rotors specially for elastic fluids
    • F04D29/28—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps
    • F04D29/284—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps for compressors
    • C—CHEMISTRY; METALLURGY
    • C21—METALLURGY OF IRON
    • C21D—MODIFYING THE PHYSICAL STRUCTURE OF FERROUS METALS; GENERAL DEVICES FOR HEAT TREATMENT OF FERROUS OR NON-FERROUS METALS OR ALLOYS; MAKING METAL MALLEABLE, e.g. BY DECARBURISATION OR TEMPERING
    • C21D2221/00—Treating localised areas of an article
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T29/00—Metal working
    • Y10T29/49—Method of mechanical manufacture
    • Y10T29/49316—Impeller making
    • Y10T29/4932—Turbomachine making
    • Y10T29/49321—Assembling individual fluid flow interacting members, e.g., blades, vanes, buckets, on rotary support member

Definitions

  • This invention relates generally to compressor wheels or impellers as may be used in a turbocharger, supercharger, and the like.
  • Locomotives equipped with internal combustion engines may require relatively high air flow rates and high manifold pressures, as may be provided by a turbocharger, to meet air quality targets while maximizing fuel economy and reliability.
  • the high boost ratios typically 3.8 or higher, may require high tip speeds on a turbocharger compressor wheel, which may lead to high levels of tensile stress in a bore area and shortened wheel life due to low cycle fatigue.
  • compressor wheels have used a through bore that extends through the center of the wheel along a rotation axis, and where the wheel may be securely mounted onto a shaft with a locking nut.
  • so called boreless compressor wheels are able to rotate at higher speeds than compressor wheels having a through bore since a through bore removes load carrying material and thereby increases the stress level in the remaining material. That is, more wheel material exists at a point of maximum centrifugal load that results in higher load carrying capability.
  • a threaded counterbore is provided in a hub extension for receiving the shaft.
  • the counterbore must terminate well short of the plane indicative of typical maximum stress to avoid the high level of stress at that location. Since the length of the shaft/threaded interface is generally constant for any given application, the foregoing arrangement (that causes the designer to position such an interface away from the high stress plane) may result in excessive overhang of the compressor wheel. This detrimentally affects rotor dynamics and increases the axial length of the hub extension, thus increasing the overall footprint of the compressor wheel and turbocharger.
  • aspects of the present invention propose to improve compressor life by using a hub with a counterbore including a base surface treated to impart residual compressive stresses for enhanced endurance to stress-induced fatigue.
  • the surface treatment allows extending the counterbore relatively closer to a plane indicative of typical maximum stress. This design flexibility advantageously allows avoiding or reducing overhang of the compressor wheel, thereby improving rotor dynamics and reducing the axial length of the hub, and the overall foot print of the compressor wheel and turbocharger.
  • the present invention fulfills the foregoing needs by providing in one aspect thereof, a method of manufacturing a compressor wheel.
  • the method allows providing a hub extension of the compressor wheel that defines a counterbore.
  • the method further allows imparting residual compressive stresses to a base surface of the counterbore.
  • the present invention further fulfills the foregoing needs by providing a compressor wheel comprising a hub including a hub extension that defines a counterbore.
  • the counterbore includes a base surface and the base surface of the counterbore is treated to impart residual compressive stresses thereto.
  • FIG. 1 illustrates a cutaway view of an exemplary turbocharger that may benefit from the teachings of the present invention.
  • FIG. 2 shows a cross-sectional view of an exemplary compressor wheel embodying aspects of the present invention.
  • FIG. 3 shows configurational details regarding the compressor wheel of FIG. 2 that allow positioning a mounting counterbore relatively closer to a plane indicative of typical maximum stress of the wheel.
  • FIG. 4 shows a rotatable shaft assembled into a counterbore embodying aspects of the present invention.
  • FIG. 1 shows a cutaway view of an exemplary turbocharger ( 10 ) that may benefit from the teachings of the present invention.
  • Turbocharger ( 10 ) generally comprises respective compressor and turbine stages ( 12 ) and ( 14 ) including a compressor wheel ( 16 ) and a turbine wheel ( 18 ) coupled through a rotatable shaft ( 20 ).
  • the turbine wheel ( 18 ) is disposed within a turbine housing, which includes an inlet for receiving exhaust gases from an internal combustion engine (not shown).
  • the turbine housing guides the engine exhaust gases for communication with and expansion through the turbine wheel ( 18 ) for rotatably driving the turbine wheel.
  • the turbine wheel rotatably drives the shaft ( 20 ) and compressor wheel ( 16 ), as may be disposed within a compressor housing.
  • the compressor wheel ( 16 ) and housing allow drawing in and compressing ambient air for supply to the intake of the engine.
  • Compressor wheel ( 16 ) includes a hub portion ( 21 ).
  • the hub portion ( 21 ) defines a front face surface ( 22 ) for the compressor wheel ( 16 ), and supports a plurality of circumferentially spaced apart compressor blades ( 23 ) (only two of which are visible in FIG. 2 ) extending both radially outwardly and axially thereon.
  • the hub portion ( 21 ) also includes a radially enlarged disc-like portion ( 24 ) which serves to support the compressor blades ( 23 ) as well as to define a floor surface ( 25 ) for the air flow channels defined between blades ( 23 ).
  • the disc-like portion ( 24 ) also defines a radially outer circumferential surface ( 26 ) for hub ( 21 ), as well as an axially disposed back side or back face surface ( 27 ).
  • a plane indicative of typical maximum stress ( 30 ) typically exists substantially in axial alignment with the maximum radial extent of the hub ( 21 ). That is, the plane of maximum stress ( 30 ) is typically coincident with surface 26 and reaches a maximum at the point where the rotation axis ( 34 ) transects plane ( 30 ), approximately at point ( 31 ).
  • compressor wheel ( 16 ) includes a hub extension ( 38 ) integrally defined by hub ( 21 ) and extending axially away from plane ( 30 ).
  • Hub extension ( 38 ) defines an axially extending counterbore ( 36 ).
  • the inventors of the present invention have innovatively recognized that one may advantageously improve rotor dynamics as well as reduce the axial length of the compressor wheel when a base surface ( 40 ) of counterbore ( 36 ) is treated to impart residual compressive stresses to such a base surface.
  • techniques such as cold working techniques, that may be used to treat the counterbore base surface may comprise shot peening, laser peening, glass beading, roll burnishing, etc.
  • Cold working provides plastic deformation of a metal (e.g., aluminum) below its annealing temperature to cause permanent strain hardening.
  • Peening means to compress a portion of a surface by forming a depression or indentation on the surface.
  • Peening equipment generally is utilized to create a compressively stressed protection layer at the outer surface of a workpiece.
  • the protection layer considerably increases the resistance of the workpiece to fatigue failure.
  • a shot used in shot peening may comprise spherical particles constructed from a hard metal or any other suitable material. With shot peening systems, a stream of shot particles traveling at a high velocity is directed at an outer surface of a workpiece, e.g., the base of the counterbore. Each shot particle that impacts with sufficient force upon the outer surface of the workpiece causes plastic deformation of the surface and a dimple is formed therein. In this manner, a compressively stressed layer is formed at the outer surface of the workpiece to increase fatigue strength of the workpiece.
  • a laser beam from a laser beam source is used to produce a strong localized compressive force on a surface.
  • Laser peening may be utilized in lieu of shot peening to create a compressively stressed protection layer at the outer surface of a workpiece. This type of treatment also considerably increases the resistance of the workpiece to fatigue failure. Thus, peening is typically a very effective means for producing surface compression residual stress, and therefore, prolonging the useful life of the workpiece.
  • the surface treatment of the base of the counterbore allows extending the base surface ( 40 ) of counterbore ( 36 ) relatively closer to the plane ( 30 ) indicative of typical maximum stress.
  • This is exemplarily illustrated in FIG. 3 by the representation of the counterbore base ( 40 ′) relative to the representation of the counterbore base ( 40 ).
  • This design flexibility advantageously allows avoiding or reducing overhang of the compressor wheel, thereby improving rotor dynamics and reducing the axial length of the hub extension, and the overall foot print of the compressor wheel and turbocharger.
  • the base ( 40 ) of counterbore ( 36 ) is configured to extend a distance L towards plane ( 30 )
  • this would allow reducing the axial length of the hub extension ( 38 ) by distance L.
  • counterbore ( 36 ) includes alignment pilots ( 42 ) disposed to facilitate the centering of the shaft ( 20 ) received in counterbore ( 36 ). That is, alignment pilots ( 42 ) are configured to minimize eccentricity of shaft ( 20 ) relative to the walls of the counterbore.
  • the compressor wheel, shaft, and thrust collar ( 44 ) may rotate relative to a bearing configured to provide radial support to the rotating structures.

Landscapes

  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Crystallography & Structural Chemistry (AREA)
  • Materials Engineering (AREA)
  • Metallurgy (AREA)
  • Organic Chemistry (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
  • Supercharger (AREA)
US11/803,206 2004-11-13 2007-05-14 Compressor wheel Abandoned US20080008595A1 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
US12/731,741 US8641380B2 (en) 2004-11-13 2010-03-25 Compressor wheel

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
GBGB0425088.2 2004-11-13
GB0425088A GB0425088D0 (en) 2004-11-13 2004-11-13 Compressor wheel
PCT/GB2005/004316 WO2006051285A1 (en) 2004-11-13 2005-11-09 Compressor wheel

Related Parent Applications (1)

Application Number Title Priority Date Filing Date
PCT/GB2005/004316 Continuation WO2006051285A1 (en) 2004-11-13 2005-11-09 Compressor wheel

Related Child Applications (1)

Application Number Title Priority Date Filing Date
US12/731,741 Continuation US8641380B2 (en) 2004-11-13 2010-03-25 Compressor wheel

Publications (1)

Publication Number Publication Date
US20080008595A1 true US20080008595A1 (en) 2008-01-10

Family

ID=33523680

Family Applications (2)

Application Number Title Priority Date Filing Date
US11/803,206 Abandoned US20080008595A1 (en) 2004-11-13 2007-05-14 Compressor wheel
US12/731,741 Expired - Fee Related US8641380B2 (en) 2004-11-13 2010-03-25 Compressor wheel

Family Applications After (1)

Application Number Title Priority Date Filing Date
US12/731,741 Expired - Fee Related US8641380B2 (en) 2004-11-13 2010-03-25 Compressor wheel

Country Status (8)

Country Link
US (2) US20080008595A1 (zh)
EP (1) EP1809907B1 (zh)
JP (1) JP2008519933A (zh)
KR (1) KR20070084157A (zh)
CN (1) CN101057078B (zh)
DE (1) DE602005019456D1 (zh)
GB (1) GB0425088D0 (zh)
WO (1) WO2006051285A1 (zh)

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20100104457A1 (en) * 2008-10-25 2010-04-29 Bosch Mahle Turbo Systems Gmbh & Co.Kg Turbocharger
US20150204331A1 (en) * 2014-01-17 2015-07-23 Borgwarner Inc. Method for connecting a compressor wheel to a shaft of a supercharging device
US20160122536A1 (en) * 2014-10-31 2016-05-05 Hyundai Motor Company Chemical resistant polymer resin composition for vehicle overhead console
WO2018181086A1 (ja) * 2017-03-30 2018-10-04 三菱重工コンプレッサ株式会社 インペラ、インペラの製造方法、及び、回転機械
US10781701B2 (en) 2016-06-01 2020-09-22 Mitsubishi Heavy Industries Engine & Turbocharger, Ltd. Impeller for rotary machine, compressor, forced induction device, and method for manufacturing impeller for rotary machine

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US9732633B2 (en) 2015-03-09 2017-08-15 Caterpillar Inc. Turbocharger turbine assembly
US9638138B2 (en) 2015-03-09 2017-05-02 Caterpillar Inc. Turbocharger and method
US9915172B2 (en) 2015-03-09 2018-03-13 Caterpillar Inc. Turbocharger with bearing piloted compressor wheel
US9822700B2 (en) 2015-03-09 2017-11-21 Caterpillar Inc. Turbocharger with oil containment arrangement
US9777747B2 (en) 2015-03-09 2017-10-03 Caterpillar Inc. Turbocharger with dual-use mounting holes
US10006341B2 (en) 2015-03-09 2018-06-26 Caterpillar Inc. Compressor assembly having a diffuser ring with tabs
US9683520B2 (en) 2015-03-09 2017-06-20 Caterpillar Inc. Turbocharger and method
US9903225B2 (en) 2015-03-09 2018-02-27 Caterpillar Inc. Turbocharger with low carbon steel shaft
US9752536B2 (en) 2015-03-09 2017-09-05 Caterpillar Inc. Turbocharger and method
US9890788B2 (en) 2015-03-09 2018-02-13 Caterpillar Inc. Turbocharger and method
US9810238B2 (en) 2015-03-09 2017-11-07 Caterpillar Inc. Turbocharger with turbine shroud
US9650913B2 (en) 2015-03-09 2017-05-16 Caterpillar Inc. Turbocharger turbine containment structure
US10066639B2 (en) 2015-03-09 2018-09-04 Caterpillar Inc. Compressor assembly having a vaneless space
US9739238B2 (en) 2015-03-09 2017-08-22 Caterpillar Inc. Turbocharger and method
US9879594B2 (en) 2015-03-09 2018-01-30 Caterpillar Inc. Turbocharger turbine nozzle and containment structure
CN106321498A (zh) * 2015-06-26 2017-01-11 上海优耐特斯压缩机有限公司 一种高速电机的离心压缩机的轴向止推轴承结构
DE102015214864A1 (de) 2015-08-04 2017-02-09 Bosch Mahle Turbo Systems Gmbh & Co. Kg Verdichterrad mit welligen Radrücken
US10883513B2 (en) * 2016-03-30 2021-01-05 Mitsubishi Heavy Industries Engine & Turbocharger, Ltd. Impeller, rotary machine, and turbocharger
EP3282130A1 (en) * 2016-08-10 2018-02-14 Siemens Aktiengesellschaft Layer system, impeller, method to produce
CN112343857A (zh) * 2019-08-07 2021-02-09 维湃科技投资(中国)有限公司 涡轮增压器及一种组装涡轮增压器的方法
US11408434B2 (en) 2019-12-10 2022-08-09 Ingersoll-Rand Industrial U.S., Inc. Centrifugal compressor impeller with nonlinear backwall
US11648632B1 (en) 2021-11-22 2023-05-16 Garrett Transportation I Inc. Treatment process for a centrifugal compressor wheel to extend low-cycle fatigue life

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US20040057834A1 (en) * 2001-02-09 2004-03-25 Masami Shimizu Connection method for turbo charger turbine shaft
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Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20100104457A1 (en) * 2008-10-25 2010-04-29 Bosch Mahle Turbo Systems Gmbh & Co.Kg Turbocharger
US9631634B2 (en) * 2008-10-25 2017-04-25 Bosch Mahle Turbo Systems Gmbh & Co. Kg Turbocharger with friction-increasing coating
US20150204331A1 (en) * 2014-01-17 2015-07-23 Borgwarner Inc. Method for connecting a compressor wheel to a shaft of a supercharging device
US20160122536A1 (en) * 2014-10-31 2016-05-05 Hyundai Motor Company Chemical resistant polymer resin composition for vehicle overhead console
US10781701B2 (en) 2016-06-01 2020-09-22 Mitsubishi Heavy Industries Engine & Turbocharger, Ltd. Impeller for rotary machine, compressor, forced induction device, and method for manufacturing impeller for rotary machine
WO2018181086A1 (ja) * 2017-03-30 2018-10-04 三菱重工コンプレッサ株式会社 インペラ、インペラの製造方法、及び、回転機械

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US8641380B2 (en) 2014-02-04
EP1809907A1 (en) 2007-07-25
KR20070084157A (ko) 2007-08-24
US20100319344A1 (en) 2010-12-23
EP1809907B1 (en) 2010-02-17
CN101057078B (zh) 2012-02-22
DE602005019456D1 (de) 2010-04-01
JP2008519933A (ja) 2008-06-12
GB0425088D0 (en) 2004-12-15
WO2006051285A1 (en) 2006-05-18
CN101057078A (zh) 2007-10-17

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