US2471174A - Centrifugal compressor stability means - Google Patents

Centrifugal compressor stability means Download PDF

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Publication number
US2471174A
US2471174A US743549A US74354947A US2471174A US 2471174 A US2471174 A US 2471174A US 743549 A US743549 A US 743549A US 74354947 A US74354947 A US 74354947A US 2471174 A US2471174 A US 2471174A
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impeller
diffuser
end member
blades
recirculation
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US743549A
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William E Trumpler
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CLARK BROS Co Inc
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CLARK BROS CO Inc
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    • 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
    • F04D29/30—Vanes
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D17/00—Radial-flow pumps, e.g. centrifugal pumps; Helico-centrifugal pumps
    • F04D17/08—Centrifugal pumps
    • F04D17/10—Centrifugal pumps for compressing or evacuating
    • 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
    • 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
    • F04D29/66—Combating cavitation, whirls, noise, vibration or the like; Balancing
    • F04D29/68—Combating cavitation, whirls, noise, vibration or the like; Balancing by influencing boundary layers
    • F04D29/681—Combating cavitation, whirls, noise, vibration or the like; Balancing by influencing boundary layers especially adapted for elastic fluid pumps

Definitions

  • This invention relates to centrifugal compresimpeller, of a tendency to discharge at higherl velocity at one end than at the other, attained as by constructing the impeller of greater diameter at the higher velocity end; and location of the recirculation flow path adjacent the other end of the impeller, at its periphery-so that, generally, the recirculation lflow path is displaced from the principal path of discharge from the impeller into the diffuser.
  • Fig. l is a typical sectional view of pertinent parts of a compressor embodying the invention, the axis of the compressor being disposed in the plane of the section, and
  • Fig. 2 is an endwise fragmentary view of the impeller of Fig. 1.
  • A is the shaft of the compressor on which is mounted, to be driven thereby, an impeller generally indicated at B.
  • C represents generally diffuser means into which the impeller B discharges; it being understood, as well known in the art, that the diffuser C is stationary and associated with bearings for the shaft A, and further that the parts illustrated may represent but one of several stages of the compressor.
  • the impeller'B comprises a pair of end members I and 2 between which extend a number of blades 3 and to both of which the blades are secured.
  • the manner of such blade securement is not materia1 to this invention, but as here shown it includes flanges on the blades bearing against and connected to the end member faces as by rivets indicated Fig. 2.
  • the end member I includes a hub portion extending to the shaft A and there having driven connection by means not appearing in the draw 6 Claims. (Cl. 230-127) ing; and the end member 2 is in the form of an annular disc, to provide a central inlet opening.
  • the blades 3 support the disc end member 2 on the hub end member I, and are disposed to have their principal extent radially and longitudinally of the shaft A, but with rearward slope with reference to the direction of rotation as indicated by the arrow, Fig. 2.
  • the diffuser C comprises a pair of walls 5 and 6 spaced to provide a diffuser passage 1 annular about the impeller to receive the discharge therefrom.
  • means are provided for stabilizing compressor operation under conditions of low demand.
  • the outer diameter of the hub end member lof the impeller is somewhat greater than that of the disc end member 2; and at their outer extremities the blades 3 are so contoured, as at 3a, that each blade is radially coextensive with each end member where the blade joins the latter.
  • the outer extremity of the blade is, for the major portion of its axial length, coextensive with the hub end member I, the blade extremity joining the disc end member 2 with slope as indicated in the drawings.
  • the blades may be slightly canted as indicated Fig. 2, so that their effective edges along the disc end member 2 have slight lead over those along the hub end member I.
  • impeller construction The result of such impeller construction is that the impeller will have a tendency to discharge at higher velocity adjacent its hub end member I than adjacent its disc end member 2; -such tendency effectively increasing as demand upon the compressor decreases, and substantially disappearing as the maximum impeller output is attained.
  • its wall 5, corresponding to the disc end member 2 of the impeller B, is ,deformed to provide an cess commences immediately adjacent the periphery of the disc end member 2, becomes maximum slightly downstream thereof approximately opposite the periphery of the hub end member I', and thence gradually merges into the straight principal wall part bounding the passage 1.
  • a recirculation iiow path is provided as indicated by the small arrows Fig. 1, leading, generally, radially from the impeller, thence toward the diffuser wall 5, thence radially inwardly within the recess 5a, and thence returning to the impeller radially short of its radial extremity; such recirculation path being displaced, endwise of the impeller, and to the left Fig. 1, from the principal straight iiow path from the impeller to the diffuser.
  • the amount of flow in the recirculation path will automatically vary with the demand upon the impeller, recirculation increasing at light impeller loads, and being negligible at full compressor load.
  • the invention provides, for recirculation, a secondary endwise inlet to the impeller located thereabout and slightly within the radial impeller extremity which is at the opposite end of the impeller, the diffuser recess directing recirculation flow to the impeller at such secondary inlet.
  • a centrifugal compressor including cooperative impeller and diffuser means, said impeller having a. pair of circular end members with blades disposed therebetween, and said diiuser -means having a pair of walls disposed to receive therebetween discharge from said impeller, one of said impeller end members being of less diameter than the other, and the corresponding diiuser wall being annularly recessed thereadj acent, to provide a flow path for recirculation at low capacity operation of said compressor.
  • a centrifugal compressor including cooperative impeller and diiuser means, said impeller having blades and said diifuser means having a pair of walls disposed to receive therebetween discharge from said impeller, said blades, endwise of the compressor being of less radial extent adjacent one of said diffuser walls than the other, and said diffuser wall being recessed adjacent the impeller periphery to provide a recirculation ow path.
  • a centrifugal compressor includingv cooperative impeller and diifuser means, said impeller having a pair of circular end members with blades disposed therebetween, and said diffuser means having a pair of walls disposed to receive therebetween discharge from said impeller, one of said CTI end members and the-adjacent portions of said blades extending radially short of the other end member and its adjacent blade portions, and the diiuser wall adjacent said shorter end member being recessed opposite the periphery of said impeller, to provide a recirculation W path.
  • a centrifugal compressor including cooperative impeller and diffuser means, said impeller having a pair of circular end members, one of said end members having a hub portion and the other being of lesser outside diameter and having a central inlet opening, and said impeller including blades extending between said end members, said diffuser means having a pair of walls disposed to receive therebetween discharge from said impeller, the diffuser wall nearer said smaller end member being recessed adjacent the periphery thereof, toprovide a recirculation flow path.
  • a centrifugal compressor having cooperative impeller and di'user means, said impeller having blades providing peripheral discharge and said diifuser having a passage arranged to receive said discharge, said impeller having less radial extent at one end than at the other, the wall of said diffuser nearer the lesser end of the impeller being recessed adjacent the impeller periphery,
  • a centrifugal compressor including cooperative impeller and diffuser means, said vimpeller having end members and blades therebetween and being of less radial extent at one end than at the other to provide a secondary recirculation inlet endwise of the impeller peripherally about and immediately radially beyond the lesser impeller end, and said diffuser having a recess adjacent the periphery of said lesser impeller end arranged to diret recirculation flow toward said secondary inle WILLIAM E. TRUMPLER.

Description

Patented May 24, 1949 2,411,174 cEN'rmFUGAL COMPRESSOR s'miu'rr MEAN William E. Trumpler, Olean, N. Y., assignor to Clark Bros. Co., Inc., Olean, N. Y., a corporation of New York Application April 24, 1947, Serial No. 743,549
This invention relates to centrifugal compresimpeller, of a tendency to discharge at higherl velocity at one end than at the other, attained as by constructing the impeller of greater diameter at the higher velocity end; and location of the recirculation flow path adjacent the other end of the impeller, at its periphery-so that, generally, the recirculation lflow path is displaced from the principal path of discharge from the impeller into the diffuser.
Further objects and advantages will be apparent from the following description taken in connection with the accompanying drawing, wherein Fig. l is a typical sectional view of pertinent parts of a compressor embodying the invention, the axis of the compressor being disposed in the plane of the section, and
Fig. 2 is an endwise fragmentary view of the impeller of Fig. 1.
With reference now to the drawings, A is the shaft of the compressor on which is mounted, to be driven thereby, an impeller generally indicated at B. C represents generally diffuser means into which the impeller B discharges; it being understood, as well known in the art, that the diffuser C is stationary and associated with bearings for the shaft A, and further that the parts illustrated may represent but one of several stages of the compressor.
More particularly as to the impeller'B, it comprises a pair of end members I and 2 between which extend a number of blades 3 and to both of which the blades are secured. The manner of such blade securement is not materia1 to this invention, but as here shown it includes flanges on the blades bearing against and connected to the end member faces as by rivets indicated Fig. 2.
The end member I includes a hub portion extending to the shaft A and there having driven connection by means not appearing in the draw 6 Claims. (Cl. 230-127) ing; and the end member 2 is in the form of an annular disc, to provide a central inlet opening.
The blades 3 support the disc end member 2 on the hub end member I, and are disposed to have their principal extent radially and longitudinally of the shaft A, but with rearward slope with reference to the direction of rotation as indicated by the arrow, Fig. 2.
The diffuser C comprises a pair of walls 5 and 6 spaced to provide a diffuser passage 1 annular about the impeller to receive the discharge therefrom.
:What has thus far been described is generally old and well known in the art. Inv its operation, when the impeller B is driven, centrifugal force will cause flow axially as indicated by the arrow A, thence radially as indicated by the arrow B to the 'impeller periphery. Therefrorn flow is divergently through the passage 1 of the diffuser, as indicated by the arrow C, the diffuser serving to convert kinetic energy imparted by the impeller, into pressure energy at the extremity of the passage 1.
According to this invention, means are provided for stabilizing compressor operation under conditions of low demand.
To this end, as here shown as to the impeller B, the outer diameter of the hub end member lof the impeller is somewhat greater than that of the disc end member 2; and at their outer extremities the blades 3 are so contoured, as at 3a, that each blade is radially coextensive with each end member where the blade joins the latter.
Preferably, the outer extremity of the blade is, for the major portion of its axial length, coextensive with the hub end member I, the blade extremity joining the disc end member 2 with slope as indicated in the drawings. Preferably also, the blades may be slightly canted as indicated Fig. 2, so that their effective edges along the disc end member 2 have slight lead over those along the hub end member I.
The result of such impeller construction is that the impeller will have a tendency to discharge at higher velocity adjacent its hub end member I than adjacent its disc end member 2; -such tendency effectively increasing as demand upon the compressor decreases, and substantially disappearing as the maximum impeller output is attained.
As to the diffuser C, according to this invention, its wall 5, corresponding to the disc end member 2 of the impeller B, is ,deformed to provide an cess commences immediately adjacent the periphery of the disc end member 2, becomes maximum slightly downstream thereof approximately opposite the periphery of the hub end member I', and thence gradually merges into the straight principal wall part bounding the passage 1.
The result of the arrangement described is that, at light loads on the compressor, a recirculation iiow path is provided as indicated by the small arrows Fig. 1, leading, generally, radially from the impeller, thence toward the diffuser wall 5, thence radially inwardly within the recess 5a, and thence returning to the impeller radially short of its radial extremity; such recirculation path being displaced, endwise of the impeller, and to the left Fig. 1, from the principal straight iiow path from the impeller to the diffuser.
The amount of flow in the recirculation path will automatically vary with the demand upon the impeller, recirculation increasing at light impeller loads, and being negligible at full compressor load.
It may be observed that, in eifect, the invention provides, for recirculation, a secondary endwise inlet to the impeller located thereabout and slightly within the radial impeller extremity which is at the opposite end of the impeller, the diffuser recess directing recirculation flow to the impeller at such secondary inlet.
What I claim is:
1. A centrifugal compressor including cooperative impeller and diffuser means, said impeller having a. pair of circular end members with blades disposed therebetween, and said diiuser -means having a pair of walls disposed to receive therebetween discharge from said impeller, one of said impeller end members being of less diameter than the other, and the corresponding diiuser wall being annularly recessed thereadj acent, to provide a flow path for recirculation at low capacity operation of said compressor.
2. A centrifugal compressor including cooperative impeller and diiuser means, said impeller having blades and said diifuser means having a pair of walls disposed to receive therebetween discharge from said impeller, said blades, endwise of the compressor being of less radial extent adjacent one of said diffuser walls than the other, and said diffuser wall being recessed adjacent the impeller periphery to provide a recirculation ow path.
3. A centrifugal compressor includingv cooperative impeller and diifuser means, said impeller having a pair of circular end members with blades disposed therebetween, and said diffuser means having a pair of walls disposed to receive therebetween discharge from said impeller, one of said CTI end members and the-adjacent portions of said blades extending radially short of the other end member and its adjacent blade portions, and the diiuser wall adjacent said shorter end member being recessed opposite the periphery of said impeller, to provide a recirculation W path.
4. A centrifugal compressor including cooperative impeller and diffuser means, said impeller having a pair of circular end members, one of said end members having a hub portion and the other being of lesser outside diameter and having a central inlet opening, and said impeller including blades extending between said end members, said diffuser means having a pair of walls disposed to receive therebetween discharge from said impeller, the diffuser wall nearer said smaller end member being recessed adjacent the periphery thereof, toprovide a recirculation flow path.
5. In a centrifugal compressor having cooperative impeller and di'user means, said impeller having blades providing peripheral discharge and said diifuser having a passage arranged to receive said discharge, said impeller having less radial extent at one end than at the other, the wall of said diffuser nearer the lesser end of the impeller being recessed adjacent the impeller periphery,
, to provide a recirculation flow path.
6. A centrifugal compressor including cooperative impeller and diffuser means, said vimpeller having end members and blades therebetween and being of less radial extent at one end than at the other to provide a secondary recirculation inlet endwise of the impeller peripherally about and immediately radially beyond the lesser impeller end, and said diffuser having a recess adjacent the periphery of said lesser impeller end arranged to diret recirculation flow toward said secondary inle WILLIAM E. TRUMPLER.
REFERENCES CITED The following references are of record in the le of this patent:
UNITED STATESl PATENTS Number Name Date 1,161,926 Criqui Nov. 30, 1915 2,096,883 I Clason Oct. 26, 1937 2,245,179 Boivie June 10, 1941 2,362,514 Warner Nov. 14, 1944 2,399,072 Thompson Apr. 23, 1946 FOREIGN PATENTS Number Country Date 318,263 Great Britain Feb. 27, 1930
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Cited By (24)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2814434A (en) * 1952-11-07 1957-11-26 Mcculloch Motors Corp Diffuser
US2992617A (en) * 1958-10-23 1961-07-18 Worthington Corp Centrifugal pump with self-priming characteristics
US3904306A (en) * 1973-07-05 1975-09-09 Thune Eureka As Two-way impeller in a centrifugal pump having vertical drive shaft
DE2642603A1 (en) * 1975-09-25 1977-03-31 Rolls Royce 1971 Ltd COMPRESSOR HOUSING FOR A GAS TURBINE ENGINE
FR2421291A1 (en) * 1978-03-28 1979-10-26 Howden James & Co Ltd IMPROVEMENTS TO FANS OR SIMILAR APPLIANCES
US4749332A (en) * 1982-04-21 1988-06-07 General Electric Company Method and apparatus for degrading antimisting fuel
US4917571A (en) * 1984-03-20 1990-04-17 John Hyll Flow-stabilizing volute pump and liner
US5064344A (en) * 1989-11-01 1991-11-12 Sundstrand Corporation Partial throat diffuser
US5127800A (en) * 1984-03-20 1992-07-07 Baker Hughes Incorporated Flow-stabilizing volute pump and liner
EP0602558A1 (en) * 1992-12-16 1994-06-22 Alcatel SEL Aktiengesellschaft Apparatus for transporting a gaseous medium
EP1039142A2 (en) * 1999-03-22 2000-09-27 Abb Fläkt Oy Fan diffuser
EP1128070A2 (en) * 2000-02-23 2001-08-29 Holset Engineering Company Limited Compressor
US20050220620A1 (en) * 2004-03-31 2005-10-06 Walker Craig I Velocity profile impeller vane
US6953321B2 (en) 2002-12-31 2005-10-11 Weir Slurry Group, Inc. Centrifugal pump with configured volute
US20060275113A1 (en) * 2002-08-13 2006-12-07 Hua Chen Compressor
US20090024191A1 (en) * 2006-03-03 2009-01-22 University Of Washington Multi-cladding optical fiber scanner
WO2015076102A1 (en) * 2013-11-22 2015-05-28 株式会社Ihi Centrifugal compressor and supercharger
DE102014222877A1 (en) * 2014-11-10 2016-05-12 Siemens Aktiengesellschaft Impeller of a radial turbofan energy machine, stage
GB2539227A (en) * 2015-06-10 2016-12-14 Cummins Ltd Compressor and turbocharger
CN106662117A (en) * 2014-09-18 2017-05-10 三菱重工业株式会社 Centrifugal impeller and centrifugal compressor
US20180073520A1 (en) * 2016-09-13 2018-03-15 Bosch Mahle Turbo Systems Gmbh & Co. Kg Charging device
CN111379744A (en) * 2018-12-25 2020-07-07 三菱重工业株式会社 Centrifugal rotary machine
US11371524B2 (en) * 2018-03-20 2022-06-28 Zhongshan Broad-Ocean Motor Co., Ltd. Windmill and blower comprising the same
US11408439B2 (en) * 2017-03-28 2022-08-09 Mitsubishi Heavy Industries Engine & Turbocharger, Ltd. Centrifugal compressor and turbocharger

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1161926A (en) * 1914-09-03 1915-11-30 Albert A Criqui Centrifugal fan.
GB318263A (en) * 1928-08-31 1930-02-27 Gen Electric Improvements in and relating to turbo-compressors
US2096883A (en) * 1933-07-19 1937-10-26 Electrolux Corp Vacuum cleaner
US2245179A (en) * 1938-04-08 1941-06-10 Electrolux Corp Vacuum cleaner
US2362514A (en) * 1941-06-03 1944-11-14 Gen Electric Centrifugal compressor
US2399072A (en) * 1944-10-18 1946-04-23 Gen Electric Centrifugal compressor

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1161926A (en) * 1914-09-03 1915-11-30 Albert A Criqui Centrifugal fan.
GB318263A (en) * 1928-08-31 1930-02-27 Gen Electric Improvements in and relating to turbo-compressors
US2096883A (en) * 1933-07-19 1937-10-26 Electrolux Corp Vacuum cleaner
US2245179A (en) * 1938-04-08 1941-06-10 Electrolux Corp Vacuum cleaner
US2362514A (en) * 1941-06-03 1944-11-14 Gen Electric Centrifugal compressor
US2399072A (en) * 1944-10-18 1946-04-23 Gen Electric Centrifugal compressor

Cited By (41)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2814434A (en) * 1952-11-07 1957-11-26 Mcculloch Motors Corp Diffuser
US2992617A (en) * 1958-10-23 1961-07-18 Worthington Corp Centrifugal pump with self-priming characteristics
US3904306A (en) * 1973-07-05 1975-09-09 Thune Eureka As Two-way impeller in a centrifugal pump having vertical drive shaft
DE2642603A1 (en) * 1975-09-25 1977-03-31 Rolls Royce 1971 Ltd COMPRESSOR HOUSING FOR A GAS TURBINE ENGINE
FR2421291A1 (en) * 1978-03-28 1979-10-26 Howden James & Co Ltd IMPROVEMENTS TO FANS OR SIMILAR APPLIANCES
US4749332A (en) * 1982-04-21 1988-06-07 General Electric Company Method and apparatus for degrading antimisting fuel
US4917571A (en) * 1984-03-20 1990-04-17 John Hyll Flow-stabilizing volute pump and liner
US5127800A (en) * 1984-03-20 1992-07-07 Baker Hughes Incorporated Flow-stabilizing volute pump and liner
US5064344A (en) * 1989-11-01 1991-11-12 Sundstrand Corporation Partial throat diffuser
EP0602558A1 (en) * 1992-12-16 1994-06-22 Alcatel SEL Aktiengesellschaft Apparatus for transporting a gaseous medium
EP1039142A2 (en) * 1999-03-22 2000-09-27 Abb Fläkt Oy Fan diffuser
EP1039142A3 (en) * 1999-03-22 2002-05-08 Abb Fläkt Oy Fan diffuser
EP1128070A2 (en) * 2000-02-23 2001-08-29 Holset Engineering Company Limited Compressor
EP1128070A3 (en) * 2000-02-23 2002-12-11 Holset Engineering Company Limited Compressor
US20060275113A1 (en) * 2002-08-13 2006-12-07 Hua Chen Compressor
US8550775B2 (en) * 2002-08-13 2013-10-08 Honeywell International Inc. Compressor
US6953321B2 (en) 2002-12-31 2005-10-11 Weir Slurry Group, Inc. Centrifugal pump with configured volute
US20050220620A1 (en) * 2004-03-31 2005-10-06 Walker Craig I Velocity profile impeller vane
US7179057B2 (en) * 2004-03-31 2007-02-20 Weir Slurry Group, Inc. Velocity profile impeller vane
US20090024191A1 (en) * 2006-03-03 2009-01-22 University Of Washington Multi-cladding optical fiber scanner
WO2015076102A1 (en) * 2013-11-22 2015-05-28 株式会社Ihi Centrifugal compressor and supercharger
JPWO2015076102A1 (en) * 2013-11-22 2017-03-16 株式会社Ihi Centrifugal compressor and turbocharger
DE112014005341B4 (en) 2013-11-22 2023-03-30 Ihi Corporation centrifugal compressor and turbocharger
CN105264236A (en) * 2013-11-22 2016-01-20 株式会社Ihi Centrifugal compressor and supercharger
CN105264236B (en) * 2013-11-22 2018-02-13 株式会社Ihi Centrifugal compressor and booster
US9874224B2 (en) 2013-11-22 2018-01-23 Ihi Corporation Centrifugal compressor and turbocharger
EP3196477A4 (en) * 2014-09-18 2018-05-02 Mitsubishi Heavy Industries, Ltd. Centrifugal impeller and centrifugal compressor
CN106662117A (en) * 2014-09-18 2017-05-10 三菱重工业株式会社 Centrifugal impeller and centrifugal compressor
WO2016074889A1 (en) 2014-11-10 2016-05-19 Siemens Aktiengesellschaft Impeller of a radial turbo fluid energy machine, and stage
DE102014222877A1 (en) * 2014-11-10 2016-05-12 Siemens Aktiengesellschaft Impeller of a radial turbofan energy machine, stage
GB2539227B (en) * 2015-06-10 2021-04-14 Cummins Ltd Compressor and turbocharger
US10578122B2 (en) 2015-06-10 2020-03-03 Cummins Ltd. Compressor and turbocharger
US20200158132A1 (en) * 2015-06-10 2020-05-21 Cummins Ltd. Compressor and turbocharger
US10907650B2 (en) * 2015-06-10 2021-02-02 Cummins Ltd. Compressor and turbocharger
GB2539227A (en) * 2015-06-10 2016-12-14 Cummins Ltd Compressor and turbocharger
US20160363129A1 (en) * 2015-06-10 2016-12-15 Cummins Ltd. Compressor and turbocharger
US20180073520A1 (en) * 2016-09-13 2018-03-15 Bosch Mahle Turbo Systems Gmbh & Co. Kg Charging device
US11408439B2 (en) * 2017-03-28 2022-08-09 Mitsubishi Heavy Industries Engine & Turbocharger, Ltd. Centrifugal compressor and turbocharger
US11371524B2 (en) * 2018-03-20 2022-06-28 Zhongshan Broad-Ocean Motor Co., Ltd. Windmill and blower comprising the same
CN111379744A (en) * 2018-12-25 2020-07-07 三菱重工业株式会社 Centrifugal rotary machine
CN111379744B (en) * 2018-12-25 2022-03-29 三菱重工业株式会社 Centrifugal rotary machine

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