US20130064659A1 - Centrifugal compressor - Google Patents

Centrifugal compressor Download PDF

Info

Publication number
US20130064659A1
US20130064659A1 US13/698,317 US201113698317A US2013064659A1 US 20130064659 A1 US20130064659 A1 US 20130064659A1 US 201113698317 A US201113698317 A US 201113698317A US 2013064659 A1 US2013064659 A1 US 2013064659A1
Authority
US
United States
Prior art keywords
shaft
helix
collector
centrifugal compressor
shaft end
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
US13/698,317
Inventor
Jürgen Geisner
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.)
Siemens AG
Original Assignee
Siemens 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 Siemens AG filed Critical Siemens AG
Assigned to SIEMENS AKTIENGESELLSCHAFT reassignment SIEMENS AKTIENGESELLSCHAFT ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: GEISNER, JUEGEN
Publication of US20130064659A1 publication Critical patent/US20130064659A1/en
Abandoned legal-status Critical Current

Links

Images

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
    • F04D29/08—Sealings
    • F04D29/083—Sealings 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
    • F04D17/00—Radial-flow pumps, e.g. centrifugal pumps; Helico-centrifugal pumps
    • F04D17/08—Centrifugal pumps
    • F04D17/10—Centrifugal pumps for compressing or evacuating
    • F04D17/12—Multi-stage pumps
    • F04D17/122—Multi-stage pumps the individual rotor discs being, one for each stage, on a common shaft and axially spaced, e.g. conventional centrifugal multi- stage 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
    • F04D29/4206—Casings; Connections of working fluid for radial or helico-centrifugal pumps 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
    • F04D29/44—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 a centrifugal compressor having a shaft which extends along a machine axis, there being a drive on the side of a collector helix, which collects a compressed fluid downstream of at least one impeller upstream of an outflow into a following machine module, which drive is arranged on a shaft end which is guided out of a housing of the centrifugal compressor, wherein an axial intake is provided on an overhang stage of the centrifugal compressor on an opposite shaft end of the shaft.
  • compressors are used in particular for compressing large volume flows (e.g. 600,000 m 3 per hour) at pressures of, for example, 8 bar.
  • the advantage of the axial intake in this case, is that the intake surface is particularly large and at the same time the maximum diameter of the impellers remains moderate such that the machine can be operated at higher speeds without overloading the materials of the rotating parts. Said machines are particularly preferred for air compression.
  • collector helix In the so-called collector helix, the compressed process fluid is collected behind the impeller and flows into a machine module downstream, for example a cooling unit.
  • a collector helix is an annular chamber realized in a slightly helical manner, the cross sectional area of which widens in the circumferential direction as it gets closer to the outlet into the following unit in the direction of rotation.
  • Said expensive geometry is due to the fact that unfavorable flow contours, which generate high pressure losses in the collector chamber, are also particularly damaging for the efficiency as a result of the increased density of said fluid.
  • the collector helix just as the housing, has a horizontal part joint which either generates an unfavorable deposition in the flow contour of the collector helix, which leads to pressure losses, or requires expensive finishing which has to be carried out in a time-intensive, individualized manner on the element which is realized, as a rule, as a cast part.
  • centrifugal compressors with an opening for compressing a fluid
  • said centrifugal compressors having a housing which has a part joint plane, which extends parallel to a machine axis and has a shaft which extends along the machine axis, having at least one impeller and one collector helix which is arranged downstream of the at least one impeller and collects the compressed fluid upstream of an outflow into a following machine module, wherein the collector helix is arranged on the first shaft end.
  • the apparatuses disclosed in said documents include a drive which is arranged on the first shaft end, wherein an axial intake of the centrifugal compressor is provided on the second shaft end.
  • the helix is realized as a single piece in the circumferential direction and is flanged to the housing of the centrifugal compressor.
  • the advantage of the collector helix being realized in a single piece is that the helix, which is realized as a rule as a cast part, does not form any deposition generated by a part joint on the flow contour which either leads to unwanted pressure losses as a result of a disturbance in the flow or requires an expensive individualized finishing process.
  • the advantage of realizing the helix in a single piece is that as a result of the high pressure of the outgoing fluid, the helix is deformed most extensively in a rotationally symmetrical manner and not, as in the case of conventional designs, severely distorted by the separation in a part joint.
  • no part joint is opened as a result of the outgoing pressure and there is also no ovalizing of the flange or of the connecting diameter of the collector helix, realized as a rule in a round manner.
  • the collector helix as carrier of a shaft seal on the side of that shaft end on which the drive of the centrifugal compressor is arranged and the shaft is guided out of the housing of the centrifugal compressor.
  • the design of the helix as carrier of the bearing there is a particularly short tolerance chain between the bearing arrangement of the shaft and the surfaces of the seal which are opposite the shaft such that particularly small seal clearances can be realized or the seal has a particularly low degree of laxity.
  • the collector helix is realized as a component closing off the housing of the centrifugal compressor on the one side similar to a cover.
  • the number of components is reduced correspondingly.
  • FIG. 1 shows a schematic representation of a longitudinal section through a compressor as claimed in the invention.
  • FIG. 1 shows a schematic longitudinal section through a compressor CO as claimed in the invention.
  • Essential component parts of the compressor CO are a housing C, a shaft SH, the impellers IM—only one of which is shown and supports an overhang stage ST, a collector helix CC which is flanged to the housing C and a drive D which rotates the shaft SH.
  • the shaft SH extends along a machine axis AX which is at the same time the axis of rotation of the drive D.
  • a process fluid F is sucked in axially by the compressor CO and enters into an overhang stage ST, continues to be compressed downstream by means of the impellers IM and enters into a last stage LST in order to be collected finally in the collector helix CC for entry into the machine module downstream.
  • the shaft SH is mounted in two radial bearings BE 1 , BE 2 .
  • the shaft SH has a first shaft end SE 1 and a second shaft end SE 2 , the first shaft end SE 1 being driven by the drive D and the second shaft end SE 2 carrying the overhang stage ST.
  • shaft end SE 1 , SE 2 in the invention refers to a region of the shaft which extends from the respective end of the shaft in the direction of the shaft center, approximately a third of the overall shaft length being designated in each case as the shaft end in the terminology of the invention.
  • the collector helix CC, the second radial bearing BE 2 and a shaft seal SHS are also arranged in the region of the first shaft end SE 1 .
  • the housing C has a part joint in the extension of the machine axis AX
  • the collector helix CC is in one piece in the extension of the machine axis or parallel thereto and is flanged to the housing C by means of first fastening elements SM 1 .
  • the collector helix CC is carrier of the second radial bearing BE 2 and of the shaft seal SHS.
  • the advantage of the one-piece design of the collector helix, which is realized as a cast part, is that said collector helix in the circumferential direction does not have any deposition, brought about otherwise by a part joint which could cause flow losses.
  • the fastening of the second radial bearing BE 2 and of the shaft seal SHS to the collector helix CC results in as short a tolerance chain as possible between the radial bearing BE 2 and the shaft seal SHS such that radial clearances of the shaft SH in the shaft seal SHS, necessary for example for thermal expansion, are able to be minimal. Particularly good efficiency can be achieved in this way.

Landscapes

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

Abstract

A centrifugal compressor includes a housing having a part joint plane which extends parallel to or along a machine axis, and a shaft extending along the machine axis and having a first shaft end and a second shaft end. At least one impeller is mounted on the shaft. A collector helix is arranged downstream of the at least one impeller and collects the compressed fluid prior to an outflow into a following machine module. The collector helix is arranged on the first shaft end. A drive is arranged on the first shaft end. An axial intake at an overhang stage of the centrifugal compressor is provided on the shaft on the second shaft end. The collector helix is realized as a single piece in the circumferential direction and is flanged to the housing of the centrifugal compressor.

Description

    CROSS REFERENCE TO RELATED APPLICATIONS
  • This application is the U.S. National Stage of International Application No. PCT/EP2011/057660, filed May 12, 2011 and claims the benefit thereof. The International Application claims the benefits of German application No. 10 2010 020 891.4 DE filed May 18, 2010. All of the applications are incorporated by reference herein in their entirety.
    • FIELD OF INVENTION
  • The invention relates to a centrifugal compressor having a shaft which extends along a machine axis, there being a drive on the side of a collector helix, which collects a compressed fluid downstream of at least one impeller upstream of an outflow into a following machine module, which drive is arranged on a shaft end which is guided out of a housing of the centrifugal compressor, wherein an axial intake is provided on an overhang stage of the centrifugal compressor on an opposite shaft end of the shaft.
    • BACKGROUND OF INVENTION
  • These types of compressors are used in particular for compressing large volume flows (e.g. 600,000 m3 per hour) at pressures of, for example, 8 bar. The advantage of the axial intake, in this case, is that the intake surface is particularly large and at the same time the maximum diameter of the impellers remains moderate such that the machine can be operated at higher speeds without overloading the materials of the rotating parts. Said machines are particularly preferred for air compression.
  • In the so-called collector helix, the compressed process fluid is collected behind the impeller and flows into a machine module downstream, for example a cooling unit. As a rule, such a collector helix is an annular chamber realized in a slightly helical manner, the cross sectional area of which widens in the circumferential direction as it gets closer to the outlet into the following unit in the direction of rotation. Said expensive geometry is due to the fact that unfavorable flow contours, which generate high pressure losses in the collector chamber, are also particularly damaging for the efficiency as a result of the increased density of said fluid. In the case of conventional compressors, the collector helix, just as the housing, has a horizontal part joint which either generates an unfavorable deposition in the flow contour of the collector helix, which leads to pressure losses, or requires expensive finishing which has to be carried out in a time-intensive, individualized manner on the element which is realized, as a rule, as a cast part.
  • Documents DE 38 35 341 A1 and U.S. Pat. No. 2,578,617 A already make known centrifugal compressors with an opening for compressing a fluid, said centrifugal compressors having a housing which has a part joint plane, which extends parallel to a machine axis and has a shaft which extends along the machine axis, having at least one impeller and one collector helix which is arranged downstream of the at least one impeller and collects the compressed fluid upstream of an outflow into a following machine module, wherein the collector helix is arranged on the first shaft end. In addition, the apparatuses disclosed in said documents include a drive which is arranged on the first shaft end, wherein an axial intake of the centrifugal compressor is provided on the second shaft end.
    • SUMMARY OF INVENTION
  • Consequently, it is the object of the invention to improve the centrifugal compressor defined in the introduction in such a manner that, on the one hand, production expenditure is reduced and, on the other hand, no high pressure losses are generated in the collector helix.
  • It is proposed as claimed in the invention that the helix is realized as a single piece in the circumferential direction and is flanged to the housing of the centrifugal compressor.
  • The advantage of the collector helix being realized in a single piece is that the helix, which is realized as a rule as a cast part, does not form any deposition generated by a part joint on the flow contour which either leads to unwanted pressure losses as a result of a disturbance in the flow or requires an expensive individualized finishing process.
  • Besides this, the advantage of realizing the helix in a single piece is that as a result of the high pressure of the outgoing fluid, the helix is deformed most extensively in a rotationally symmetrical manner and not, as in the case of conventional designs, severely distorted by the separation in a part joint. In particular, no part joint is opened as a result of the outgoing pressure and there is also no ovalizing of the flange or of the connecting diameter of the collector helix, realized as a rule in a round manner.
  • An advantageous further development of the invention provides that the helix is realized as support of a shaft bearing for the bearing arrangement of the shaft. As a result, on the one hand a particularly compact design is achieved and, on the other hand, the tolerance chain between the impellers of the shaft and opposite inside surfaces of the housing is particularly short.
  • Additionally advantageous is a design of the collector helix as carrier of a shaft seal on the side of that shaft end on which the drive of the centrifugal compressor is arranged and the shaft is guided out of the housing of the centrifugal compressor. In particular in combination with the design of the helix as carrier of the bearing, there is a particularly short tolerance chain between the bearing arrangement of the shaft and the surfaces of the seal which are opposite the shaft such that particularly small seal clearances can be realized or the seal has a particularly low degree of laxity.
  • In an expedient manner, the collector helix is realized as a component closing off the housing of the centrifugal compressor on the one side similar to a cover. The number of components is reduced correspondingly.
  • The directional specifications—axially, radially and circumferential direction—always relate to the machine axis.
    • BRIEF DESCRIPTION OF THE DRAWINGS
  • The invention is described below in more detail by way of a special exemplary embodiment with reference to a drawing, further possibilities of the conversion of the invention presenting themselves to the expert apart from said exemplary embodiment in particular from an arbitrary combination of the features defined in the dependent sub-claims. In which drawing:
  • FIG. 1 shows a schematic representation of a longitudinal section through a compressor as claimed in the invention.
    •  DETAILED DESCRIPTION OF INVENTION
  • FIG. 1 shows a schematic longitudinal section through a compressor CO as claimed in the invention. Essential component parts of the compressor CO are a housing C, a shaft SH, the impellers IM—only one of which is shown and supports an overhang stage ST, a collector helix CC which is flanged to the housing C and a drive D which rotates the shaft SH.
  • The shaft SH extends along a machine axis AX which is at the same time the axis of rotation of the drive D. A process fluid F is sucked in axially by the compressor CO and enters into an overhang stage ST, continues to be compressed downstream by means of the impellers IM and enters into a last stage LST in order to be collected finally in the collector helix CC for entry into the machine module downstream. The shaft SH is mounted in two radial bearings BE1, BE2. The shaft SH has a first shaft end SE1 and a second shaft end SE2, the first shaft end SE1 being driven by the drive D and the second shaft end SE2 carrying the overhang stage ST. The term shaft end SE1, SE2 in the invention refers to a region of the shaft which extends from the respective end of the shaft in the direction of the shaft center, approximately a third of the overall shaft length being designated in each case as the shaft end in the terminology of the invention. Apart from the torque-transmitting connection to the drive D, the collector helix CC, the second radial bearing BE2 and a shaft seal SHS are also arranged in the region of the first shaft end SE1. Whilst the housing C has a part joint in the extension of the machine axis AX, the collector helix CC is in one piece in the extension of the machine axis or parallel thereto and is flanged to the housing C by means of first fastening elements SM1. At the same time, the collector helix CC is carrier of the second radial bearing BE2 and of the shaft seal SHS. The advantage of the one-piece design of the collector helix, which is realized as a cast part, is that said collector helix in the circumferential direction does not have any deposition, brought about otherwise by a part joint which could cause flow losses. The fastening of the second radial bearing BE2 and of the shaft seal SHS to the collector helix CC results in as short a tolerance chain as possible between the radial bearing BE2 and the shaft seal SHS such that radial clearances of the shaft SH in the shaft seal SHS, necessary for example for thermal expansion, are able to be minimal. Particularly good efficiency can be achieved in this way.

Claims (3)

1-2. (canceled)
3. A centrifugal compressor for compressing a fluid, the centrifugal compressor comprising:
a housing which has a part joint plane which extends parallel to or along a machine axis,
a shaft which extends along the machine axis and has a first shaft end and a second shaft end,
at least one impeller which is mounted on the shaft,
a collector helix which is arranged downstream of the at least one impeller and collects the compressed fluid prior to an outflow into a following machine module, wherein the collector helix is arranged on the first shaft end, and
a drive which is arranged on the first shaft end,
wherein an axial intake at an overhang stage of the centrifugal compressor is provided on the shaft on the second shaft end,
wherein the collector helix is realized as a single piece in the circumferential direction and is flanged to the housing of the centrifugal compressor.
4. The centrifugal compressor as claimed in claim 3, wherein the collector helix is realized as support of a radial bearing for the bearing arrangement of the shaft.
US13/698,317 2010-05-18 2011-05-12 Centrifugal compressor Abandoned US20130064659A1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE102010020891 2010-05-18
DE102010020891.4 2010-05-18
PCT/EP2011/057660 WO2011144515A1 (en) 2010-05-18 2011-05-12 Centrifugal compressor

Publications (1)

Publication Number Publication Date
US20130064659A1 true US20130064659A1 (en) 2013-03-14

Family

ID=44312333

Family Applications (1)

Application Number Title Priority Date Filing Date
US13/698,317 Abandoned US20130064659A1 (en) 2010-05-18 2011-05-12 Centrifugal compressor

Country Status (4)

Country Link
US (1) US20130064659A1 (en)
EP (1) EP2572108B1 (en)
CN (1) CN102893033B (en)
WO (1) WO2011144515A1 (en)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20140270845A1 (en) * 2011-12-06 2014-09-18 Canon Kabushiki Kaisha Cartridge detachably mountable to main assembly of electrophotographic image forming apparatus, assembling method for drive transmitting device for photosensitive drum, and electrophotographic image forming apparatus
US9689502B2 (en) 2015-10-26 2017-06-27 Rolls-Royce Corporation Rotary exhaust valve system

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US6196809B1 (en) * 1997-03-19 2001-03-06 Hitachi, Ltd. Two-stage centrifugal compressor
US6345503B1 (en) * 2000-09-21 2002-02-12 Caterpillar Inc. Multi-stage compressor in a turbocharger and method of configuring same
US6962479B2 (en) * 2003-04-16 2005-11-08 Adrian Alexander Hubbard Compound centrifugal and screw compressor
US20090246009A1 (en) * 2008-03-31 2009-10-01 Honeywell International, Inc. Compressor scrolls for auxiliary power units
US8425187B2 (en) * 2007-10-19 2013-04-23 Siemens Aktiengesellschaft Pressure vessel having a lid
US8882457B2 (en) * 2008-11-14 2014-11-11 Atlas Copco Energas Gmbh Multistage radial turbocompressor

Family Cites Families (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE503754C (en) * 1928-04-11 1930-07-26 Siemens Schuckertwerke Akt Ges Centrifugal compressor with housing cooling
US2476191A (en) * 1945-06-15 1949-07-12 Westinghouse Electric Corp Multistage, axial flow, gas compressor
US2578617A (en) * 1946-11-15 1951-12-11 Worthington Pump & Mach Corp Multistage centrifugal compressor
DE835341C (en) * 1948-11-28 1952-03-31 Diederich Storjohann Saucepan handle
CH676487A5 (en) * 1988-10-19 1991-01-31 Proizv Ob Nevsky Z Im V I
BR0008359A (en) * 1999-01-25 2001-11-27 Elliott Turbo Housing for rotating machines, method for manufacturing a portion of housing and high pressure housing

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US6196809B1 (en) * 1997-03-19 2001-03-06 Hitachi, Ltd. Two-stage centrifugal compressor
US6345503B1 (en) * 2000-09-21 2002-02-12 Caterpillar Inc. Multi-stage compressor in a turbocharger and method of configuring same
US6962479B2 (en) * 2003-04-16 2005-11-08 Adrian Alexander Hubbard Compound centrifugal and screw compressor
US8425187B2 (en) * 2007-10-19 2013-04-23 Siemens Aktiengesellschaft Pressure vessel having a lid
US20090246009A1 (en) * 2008-03-31 2009-10-01 Honeywell International, Inc. Compressor scrolls for auxiliary power units
US8882457B2 (en) * 2008-11-14 2014-11-11 Atlas Copco Energas Gmbh Multistage radial turbocompressor

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20140270845A1 (en) * 2011-12-06 2014-09-18 Canon Kabushiki Kaisha Cartridge detachably mountable to main assembly of electrophotographic image forming apparatus, assembling method for drive transmitting device for photosensitive drum, and electrophotographic image forming apparatus
US9395679B2 (en) * 2011-12-06 2016-07-19 Canon Kabushiki Kaisha Cartridge detachably mountable to main assembly of electrophotographic image forming apparatus, assembling method for drive transmitting device for photosensitive drum, and electrophotographic image forming apparatus
US9823619B2 (en) 2011-12-06 2017-11-21 Canon Kabushiki Kaisha Cartridge detachably mountable to main assembly of electrophotographic image forming apparatus, assembling method for drive transmitting device for photosensitive drum, and electrophotographic image forming apparatus
US10635045B2 (en) 2011-12-06 2020-04-28 Canon Kabushiki Kaisha Cartridge detachably mountable to main assembly of electrophotographic image forming apparatus, assembling method for drive transmitting device for photosensitive drum, and electrophotographic image forming apparatus
US11163259B2 (en) 2011-12-06 2021-11-02 Canon Kabushiki Kaisha Cartridge detachably mountable to main assembly of electrophotographic image forming apparatus, assembling method for drive transmitting device for photosensitive drum, and electrophotographic image forming apparatus
US11619905B2 (en) 2011-12-06 2023-04-04 Canon Kabushiki Kaisha Cartridge detachably mountable to main assembly of electrophotographic image forming apparatus, assembling method for drive transmitting device for photosensitive drum, and electrophotographic image forming apparatus
US9689502B2 (en) 2015-10-26 2017-06-27 Rolls-Royce Corporation Rotary exhaust valve system

Also Published As

Publication number Publication date
WO2011144515A1 (en) 2011-11-24
EP2572108B1 (en) 2015-08-26
CN102893033A (en) 2013-01-23
EP2572108A1 (en) 2013-03-27
CN102893033B (en) 2015-06-03

Similar Documents

Publication Publication Date Title
JP6632763B2 (en) Turbo compressor with intercooler
EP2924294B1 (en) Electric motor-driven compressor having a heat shield forming a wall of a diffuser
US9976564B2 (en) Multi-stage radial compressor unit comprising gas removal during a compressor stage
US9133725B2 (en) Axial shaft seal for a turbomachine
US10094391B2 (en) Compressor housing for supercharger
CN107850080B (en) Centrifugal compressor with interstage seal arrangement
US10851792B2 (en) Diagonal fan
US20180030992A1 (en) Centrifugal compressor and geared centrifugal compressor
US20070059168A1 (en) Volute for a centrifugal compressor
US8517708B2 (en) Fuel pump with axial slide gap
WO2016051835A1 (en) Centrifugal compressor
US20140170000A1 (en) Side channel blower having a plurality of feed channels distributed over the circumference
WO2016193002A1 (en) A centrifugal refrigeration compressor
EP3168479A1 (en) Rotary machine
WO2016129039A1 (en) Supercharger
US20130064659A1 (en) Centrifugal compressor
WO2014122819A1 (en) Centrifugal compressor
JP2011208518A (en) Method of manufacturing rotor assembly, rotor assembly, and turbo compressor
EP3421808B1 (en) Rotary compressor machine
US11401944B2 (en) Impeller and centrifugal compressor
US11041497B1 (en) Centrifugal rotary machine
US10598188B2 (en) Radial compressor and turbocharger
US20120275923A1 (en) Rotor for a turbo-machine
US10883513B2 (en) Impeller, rotary machine, and turbocharger
EP3372842B1 (en) Casing assembly and rotary electric machine

Legal Events

Date Code Title Description
AS Assignment

Owner name: SIEMENS AKTIENGESELLSCHAFT, GERMANY

Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNOR:GEISNER, JUEGEN;REEL/FRAME:029309/0789

Effective date: 20121019

STCB Information on status: application discontinuation

Free format text: ABANDONED -- AFTER EXAMINER'S ANSWER OR BOARD OF APPEALS DECISION