WO2011032549A1 - Turbomachine axiale-radiale - Google Patents

Turbomachine axiale-radiale Download PDF

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Publication number
WO2011032549A1
WO2011032549A1 PCT/DE2010/050030 DE2010050030W WO2011032549A1 WO 2011032549 A1 WO2011032549 A1 WO 2011032549A1 DE 2010050030 W DE2010050030 W DE 2010050030W WO 2011032549 A1 WO2011032549 A1 WO 2011032549A1
Authority
WO
WIPO (PCT)
Prior art keywords
axial
radial
housing
partition wall
partition
Prior art date
Application number
PCT/DE2010/050030
Other languages
German (de)
English (en)
Inventor
Christoph Lange
Arno Richter
Original Assignee
Man Diesel & Turbo Se
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 Man Diesel & Turbo Se filed Critical Man Diesel & Turbo Se
Priority to US13/497,331 priority Critical patent/US20130028724A1/en
Priority to CN2010800422179A priority patent/CN102782330A/zh
Priority to JP2012529121A priority patent/JP2013505386A/ja
Priority to EP10732634A priority patent/EP2480791A1/fr
Priority to BR112012006262A priority patent/BR112012006262A2/pt
Publication of WO2011032549A1 publication Critical patent/WO2011032549A1/fr

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
    • F01D25/00—Component parts, details, or accessories, not provided for in, or of interest apart from, other groups
    • F01D25/24—Casings; Casing parts, e.g. diaphragms, casing fastenings
    • F01D25/243—Flange connections; Bolting arrangements
    • 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
    • F04D17/02—Radial-flow pumps, e.g. centrifugal pumps; Helico-centrifugal pumps having non-centrifugal stages, e.g. centripetal
    • F04D17/025—Radial-flow pumps, e.g. centrifugal pumps; Helico-centrifugal pumps having non-centrifugal stages, e.g. centripetal comprising axial flow and radial flow stages
    • 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
    • F04D25/00—Pumping installations or systems
    • F04D25/16—Combinations of two or more pumps ; Producing two or more separate gas flows

Definitions

  • the invention relates to an axial-radial flow machine having an axial part with at least one axial step and a radial part with at least one radial step.
  • An axial-radial flow machine 1 as shown in FIG. 1 has an axial part 10 with a plurality of axial steps 1 1, a radial part 20 with a
  • the partition 40 is formed with such a large wall thickness S (see FIG. 2) that deformations of the partition 40 are reduced to a permissible level.
  • FIG. 2 shows an enlarged partial view of a region A in FIG.
  • a large industrial fluid machine could have an outside dimension in FIG Radial direction RR of about 4000 mm, wherein the wall thickness S (in the axial direction AR of the partition wall 40) could be about 500 mm.
  • the invention has for its object to provide an axial-radial flow machine, wherein the partition reliably against excessive
  • Deformations is protected in the axial direction of the housing and thereby may have a smaller wall thickness than in the prior art.
  • an axial-radial flow machine comprises: an axial part having at least one axial step, a radial part having at least one radial step, a housing having an inner space passing through a partition wall extending in a radial direction of the housing in an axial direction of the housing in a first part space in which the axial part is received, and a second part space is divided, in which the radial part is received, and a shaft which extends in the axial direction through the interior of the housing and the partition wall and on the impellers of the axial part and of
  • Radial part is formed a radial gap, and wherein in the radial gap a
  • a wall thickness (in the axial direction) of the partition wall according to the invention from 500 mm to about 250 mm reduced.
  • Such a wall thickness reduction of the partition wall can thus make up a weight reduction of the axial-radial flow machine of several tons, as in the example about 25 tons.
  • the fluid guide element can be formed for example by a return or a diffuser insert of the radial part.
  • each of the fixing units has a projection bridging the radial gap in the axial direction of the housing on the dividing wall and / or the fluid-conducting element.
  • the protrusions may be integrally formed with the partition wall and / or the fluid conducting element (e.g., as sprues) or may be mounted as separate parts thereto.
  • the fixing units each have a threaded bolt which extends in the axial direction of the housing through the partition wall and the Fluidleitelement, wherein the threaded bolt with at least one of the partition wall and the Fluidleitelement in
  • Thread engagement is.
  • the threaded bolt would preferably be supported axially on the part not in each case in threaded engagement (partition wall or fluid guide element), so that here too an axial fixation of the partition in the form of an axial support would be provided on the fluid guide element, whereby axially from Axial part from acting in the direction of the radial part towards the partition forces can be reliably absorbed.
  • the threaded bolt can also be used both with the partition wall and with the fluid guide in
  • Thread engagement are, whereby a two-sided axial fixation of the partition is achieved.
  • Fixing units also each have a spacer sleeve, which in the radial gap the threaded bolt is arranged and bridges the radial gap in the axial direction of the housing.
  • the threaded bolt if desired, merely serve as a radial fixation of the spacer sleeve, since the spacer sleeve rests axially on both the partition wall and on the Fluidleitelement and thus an axial
  • Fluidleitelement provides, whereby axially acting from the axial part in the direction of the radial part towards the partition forces can be reliably intercepted.
  • the threaded bolt is formed by a threaded screw having an externally threaded shank portion and an enlarged one with respect to the shank portion
  • This embodiment of the invention realizes a two-sided axial fixation of the partition wall, wherein both axially acting in the direction of the radial part from the axial part and from the axial part of the radial part towards the partition forces acting reliably can be intercepted.
  • the threaded bolt would be for an axial support of the partition to the fluid guide against act axially in the direction of the radial part from the axial part towards acting on the partition wall forces.
  • the axial-radial flow machine is formed by an axial-radial compressor.
  • pressure-difference-based force acts axially in the direction of the radial part from the axial part towards the partition wall, since with the radial part higher pressures than with the axial part can be generated.
  • FIG. 1 shows a schematic side sectional view of an axial-radial flow machine.
  • FIG. 2 shows a schematic partial view of a region A of the axial-radial flow machine of Figure 1 according to the prior art.
  • FIG. 3 shows a schematic partial view of a region A of the axial-radial flow machine of Figure 1 according to an embodiment of the invention, seen in a first sectional plane.
  • 4 shows a schematic partial view of the area A 'of the axial-radial flow machine of Figure 1 according to an embodiment of the
  • FIG. 5 shows a schematic perspective view, in which the axial-radial flow machine according to Figure 3 and Figure 4 is shown in the region of the partition radially cut.
  • FIG. 6 shows a schematic partial view of the area A 'of the axial-radial flow machine of Figure 1 according to an embodiment of the
  • an axial-radial flow machine 1 according to an embodiment of the invention will be described with reference to FIG. 1 and FIGS.
  • the axial-radial flow machine 1 by an axial-radial compressor (a compressor with an axial compressor and a centrifugal compressor, which are combined to form a unit) is formed.
  • the axial-radial flow machine 1 has an axial part 10 with a plurality of axial stages 1 1, a radial part 20 with a plurality of radial steps 21, a housing 30 with an interior, which extends through a in a radial direction RR of the housing 30th extending partition wall 40 'in an axial direction AR of the housing 30 in a first part space 31 in which the axial part 10 is received, and a second part space 32 is divided, in which the radial part 20 is received, and a shaft 50, which in Axial direction AR through the interior of the housing 30 and the partition wall 40 'extends therethrough and are received on the wheels 12, 22 of the axial part 10 and the radial part 20.
  • the radial part 20 of the axial-radial flow machine 1 according to the invention has an axially fixed to the housing 30 here as feedback insert or
  • a plurality of in a circumferential direction UR (see Figure 5) of the housing 30 distributed fixing units 60 are arranged, each of which provide an axial fixation of the partition wall 40 'to the fluid guide 23.
  • the fixing units 60 each form a radial gap RS in the axial direction AR of the housing 30 bridging projection which, according to this embodiment and as explained in more detail below, is mounted both on the partition wall 40 'and on the Fluidleitelement 23.
  • the fixing units 60 each have one here as a threaded screw
  • Spacer sleeve 62 which is arranged in the radial gap RS on the threaded bolt 61 and which bridges the radial gap RS in the axial direction AR of the housing 30, so that the spacer sleeve 62 abuts both the partition wall 40 'and on the Fluidleitelement 23.
  • the threaded bolt 61 has a at one end of its externally threaded shank portion 61 a and a relative to the shaft portion 61 a formed enlarged head portion 61 b.
  • the threaded bolt 61 is formed from the first subspace 31 (or from the axial portion 10) through a through passage (not designated) in the partition wall 40 '. inserted so that the head portion 61 b on the side of the first subspace 31 in a recess or recess (not labeled) on the partition wall 40 'is supported and the external thread of the shaft portion 61 a with an internal thread (not designated) in the fluid guide element 23 in Intervention is.
  • the spacer sleeve 62 acts on the one hand as a spacer for an axial gap dimension of the radial gap RS and on the other hand ensures an axial
  • twelve (12) fixing units 60 are exemplarily provided, as can be seen in FIG.
  • Threaded bolt exemplarily designed as M48 threaded screw.
  • the axial-radial flow machine 1 designed as an axial-radial compressor is a large-capacity industrial machine having an exemplary outside radial dimension RR of about 4000 mm and a wall thickness S 'of the partition wall 40' of about 250 mm.
  • a weight saving compared to the exemplary axial-radial flow machine of the prior art described above with reference to FIG. 2 of approximately 25 tons is realized.
  • designed as an axial-radial compressor axial-radial flow machine 1 in the operation of this between the axial part 10 and the radial part 20 exemplary one
  • Axial-radial flow machine 1 according to the invention only about 80 percent of the maximum deformation path of the partition wall 40 of the prior art axial-radial flow machine described above with reference to Figure 2.
  • the resulting deformation greatly depends on the structure of the fluid guide member 23 of the radial member 20. That is, the fluid guide element 23 should be as stiff as possible and be able to initiate the attacking forces as well as possible into the outer region of the housing 30, as indicated by the deformation situation illustrated in FIG.
  • the inventors further discovered in investigations that the fixing units 60, in particular their spacers 62, block the flow channel formed by the radial gap RS for a working fluid to be compressed in the radial part 20 only to about 10 percent and the

Landscapes

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

Abstract

L'invention concerne une turbomachine axiale-radiale (1) comprenant: une partie axiale (10) avec au moins un étage axial (11), une partie radiale (20) avec au moins un étage radial (21), un logement (30) avec un espace intérieur qui est divisé dans une direction axiale par une cloison (401) s'étendant dans une direction radiale en un premier espace partiel (31) dans lequel la partie axiale est reçue et un deuxième espace partiel (32) dans lequel la partie radiale est reçue, et au moins un arbre (50) qui s'étend dans la direction axiale à travers l'espace intérieur et la cloison et sur lequel des roues mobiles (12, 22) de la partie axiale et de la partie radiale sont reçues, une fente radiale (RS) étant formée entre la cloison et un élément de guidage de fluide (23) de la partie radiale, voisin de la cloison, fixé axialement au logement, et une pluralité d'unités de fixation (60), qui sont réparties dans la direction périphérique et qui produisent respectivement une fixation axiale de la cloison à l'élément de guidage de fluide, étant disposés dans la fente radiale.
PCT/DE2010/050030 2009-09-21 2010-05-25 Turbomachine axiale-radiale WO2011032549A1 (fr)

Priority Applications (5)

Application Number Priority Date Filing Date Title
US13/497,331 US20130028724A1 (en) 2009-09-21 2010-05-25 Axial-radial turbomachine
CN2010800422179A CN102782330A (zh) 2009-09-21 2010-05-25 轴向-径向涡轮机
JP2012529121A JP2013505386A (ja) 2009-09-21 2010-05-25 軸流式遠心ターボ機械
EP10732634A EP2480791A1 (fr) 2009-09-21 2010-05-25 Turbomachine axiale-radiale
BR112012006262A BR112012006262A2 (pt) 2009-09-21 2010-05-25 turbomáquina axial-radial

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102009029647.6 2009-09-21
DE102009029647A DE102009029647A1 (de) 2009-09-21 2009-09-21 Axial-Radial-Strömungsmaschine

Publications (1)

Publication Number Publication Date
WO2011032549A1 true WO2011032549A1 (fr) 2011-03-24

Family

ID=42556505

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/DE2010/050030 WO2011032549A1 (fr) 2009-09-21 2010-05-25 Turbomachine axiale-radiale

Country Status (7)

Country Link
US (1) US20130028724A1 (fr)
EP (1) EP2480791A1 (fr)
JP (1) JP2013505386A (fr)
CN (1) CN102782330A (fr)
BR (1) BR112012006262A2 (fr)
DE (1) DE102009029647A1 (fr)
WO (1) WO2011032549A1 (fr)

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102013015993A1 (de) * 2013-09-26 2015-03-26 Man Diesel & Turbo Se Verdichteranordnung
RU2016145846A (ru) * 2014-05-05 2018-06-06 Эксерджи С.П.А. Радиальная турбомашина
US10267328B2 (en) 2015-07-21 2019-04-23 Rolls-Royce Corporation Rotor structure for rotating machinery and method of assembly thereof
CN110999166B (zh) * 2017-09-07 2022-07-01 南通朗恒通信技术有限公司 一种被用于无线通信的用户设备、基站中的方法和装置
JP6935312B2 (ja) * 2017-11-29 2021-09-15 三菱重工コンプレッサ株式会社 多段遠心圧縮機

Citations (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE338108C (de) * 1919-05-20 1921-06-14 Hans Kasparek Kreiselverdichter fuer hohen Druck
US2017826A (en) * 1933-02-06 1935-10-15 United Iron Works Pump
DE2048106A1 (de) * 1969-09-30 1971-04-29 Ingersoll Rand Co Turbinen Kompressoraufbau
US3733145A (en) * 1971-03-04 1973-05-15 Nevsky Mash Vand-type centrifugal machine, mainly, high-pressure compressor
US3764236A (en) * 1971-07-15 1973-10-09 Carter Co J C Modular pump
US3809493A (en) * 1970-06-08 1974-05-07 Carrier Corp Interchangeable compressor drive
US4057371A (en) * 1974-05-03 1977-11-08 Norwalk-Turbo Inc. Gas turbine driven high speed centrifugal compressor unit
US4251183A (en) * 1978-01-30 1981-02-17 The Garrett Corp. Crossover duct assembly
US4579509A (en) * 1983-09-22 1986-04-01 Dresser Industries, Inc. Diffuser construction for a centrifugal compressor
US5209652A (en) * 1991-12-06 1993-05-11 Allied-Signal, Inc. Compact cryogenic turbopump
WO2007064605A2 (fr) * 2005-11-30 2007-06-07 Dresser-Rand Company Dispositif de fermeture d'extremite pour carter de turbomachine

Family Cites Families (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3976395A (en) * 1975-09-12 1976-08-24 Igor Martynovich Kalnin Multiple-stage centrifugal compressor
JPS58120000A (ja) * 1982-01-06 1983-07-16 Hitachi Ltd 回転機械のダイヤフラム
CA1252075A (fr) * 1983-09-22 1989-04-04 Dresser Industries, Inc. Configuration de diffuseur pour compresseur centrifuge
JPH0613879B2 (ja) * 1986-04-24 1994-02-23 ヤンマーディーゼル株式会社 遠心式圧縮機のベーン固定装置
US5042970A (en) * 1989-11-28 1991-08-27 Sundstrand Corporation Fast recharge compressor
US6935838B1 (en) * 2003-03-19 2005-08-30 Hi-Bar Blowers, Inc. High pressure multi-stage centrifugal blower

Patent Citations (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE338108C (de) * 1919-05-20 1921-06-14 Hans Kasparek Kreiselverdichter fuer hohen Druck
US2017826A (en) * 1933-02-06 1935-10-15 United Iron Works Pump
DE2048106A1 (de) * 1969-09-30 1971-04-29 Ingersoll Rand Co Turbinen Kompressoraufbau
US3809493A (en) * 1970-06-08 1974-05-07 Carrier Corp Interchangeable compressor drive
US3733145A (en) * 1971-03-04 1973-05-15 Nevsky Mash Vand-type centrifugal machine, mainly, high-pressure compressor
US3764236A (en) * 1971-07-15 1973-10-09 Carter Co J C Modular pump
US4057371A (en) * 1974-05-03 1977-11-08 Norwalk-Turbo Inc. Gas turbine driven high speed centrifugal compressor unit
US4251183A (en) * 1978-01-30 1981-02-17 The Garrett Corp. Crossover duct assembly
US4579509A (en) * 1983-09-22 1986-04-01 Dresser Industries, Inc. Diffuser construction for a centrifugal compressor
US5209652A (en) * 1991-12-06 1993-05-11 Allied-Signal, Inc. Compact cryogenic turbopump
WO2007064605A2 (fr) * 2005-11-30 2007-06-07 Dresser-Rand Company Dispositif de fermeture d'extremite pour carter de turbomachine

Also Published As

Publication number Publication date
DE102009029647A1 (de) 2011-03-24
EP2480791A1 (fr) 2012-08-01
JP2013505386A (ja) 2013-02-14
BR112012006262A2 (pt) 2016-05-31
US20130028724A1 (en) 2013-01-31
CN102782330A (zh) 2012-11-14

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