EP2572108B1 - Compresseur centrifuge - Google Patents

Compresseur centrifuge Download PDF

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Publication number
EP2572108B1
EP2572108B1 EP11721272.0A EP11721272A EP2572108B1 EP 2572108 B1 EP2572108 B1 EP 2572108B1 EP 11721272 A EP11721272 A EP 11721272A EP 2572108 B1 EP2572108 B1 EP 2572108B1
Authority
EP
European Patent Office
Prior art keywords
shaft
centrifugal compressor
shaft end
spiral
housing
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.)
Not-in-force
Application number
EP11721272.0A
Other languages
German (de)
English (en)
Other versions
EP2572108A1 (fr
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
Publication of EP2572108A1 publication Critical patent/EP2572108A1/fr
Application granted granted Critical
Publication of EP2572108B1 publication Critical patent/EP2572108B1/fr
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

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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
    • F04D29/08—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 extending along a machine axis, wherein a drive on the side of a collecting spiral, the downstream of at least one impeller collects a compressed fluid from an outflow into a subsequent machine module, which drive led out at one of a housing of the centrifugal compressor Shaft end is arranged, wherein at an opposite shaft end of the shaft, an axial suction is provided at an overhang stage of the centrifugal compressor.
  • Such compressors are used in particular for compressing large volume flows (eg 600,000 m 3 per hour) to pressures of, for example, 8 bar.
  • the axial suction here has the advantage that the suction is designed to be particularly large and at the same time the maximum diameter of the wheels remains moderate, so that the machine can be operated at higher speeds without overloading the materials of the rotating parts.
  • These machines are particularly preferred for air compression.
  • the compressed process fluid collects behind the impeller and flows into a subsequent machine module, for example a refrigeration unit.
  • a collecting spiral is a slightly helically executed annular chamber whose cross-sectional area widens in the circumferential direction with increasing proximity to the outflow into the downstream aggregate in the direction of rotation, since the volume flow through the collecting space increases in the same way.
  • This elaborate geometry is due to the fact that unfavorable flow contours, which generate high pressure losses in the collecting space, are also particularly detrimental to the efficiency due to the increased density of this fluid.
  • centrifugal compressor with input for compressing a fluid having a housing having a parallel to a machine axis extending parting plane and having a shaft extending along the machine axis with at least one impeller and a collecting spiral, which is arranged downstream of the at least one impeller and collecting the compressed fluid prior to outflow into a subsequent engine module, the collection coil being disposed at the first shaft end.
  • the devices disclosed therein comprise a drive, which is arranged on the first shaft end, wherein on the second shaft end an axial suction of the centrifugal compressor is provided.
  • the invention has therefore taken on the task to improve the centrifugal compressor initially defined such that on the one hand, the manufacturing cost is reduced and on the other hand no high pressure losses are generated in the collecting spiral.
  • the spiral is formed undivided in the circumferential direction and is flanged to the housing of the centrifugal compressor.
  • the undivided design of the collecting spiral has the advantage that the spiral, which is generally designed as a casting, does not form a shoulder on the flow contour produced by a parting line, which leads to undesired pressure losses either as a result of a disruption of the flow or a complex individualized post-processing needs.
  • the undivided formation of the spiral has the advantage that deformations of the spiral due to the high pressure of the outflowing fluid largely rotationally symmetrical and not, as in conventional training, by the separation in a parting joint strongly distorted occur.
  • no parting line opens as a result of Abström horres and there is also no ovalization of the generally round flange or the connection diameter of the collecting spiral.
  • An advantageous development of the invention provides that the spiral as a carrier of a shaft bearing for the storage of Shaft is formed. As a result, on the one hand a particularly compact design is achieved and on the other hand, the tolerance chain between the wheels of the shaft and opposite inner surfaces of the housing is particularly short.
  • the collecting spiral as a 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 led out of the housing of the centrifugal compressor.
  • the formation of the spiral as the wearer of the bearing results in a particularly short tolerance chain between the bearing of the shaft and the surfaces of the seal, which face the shaft, so that particularly small sealing games can be realized or the seal a particularly low permeability Has.
  • the collecting spiral as the housing of the centrifugal compressor on one side final component as it formed a lid Accordingly, the number of components is reduced.
  • the directional data axial, radial, circumferential direction always refer to the machine axis.
  • FIG. 1 shows a schematic longitudinal section through a compressor CO according to the invention.
  • Essential components of the compressor CO are a housing C, a shaft SH, the wheels IM, of which only one is shown and carries an overhang ST, a to the housing C flanged collection spiral CC and a drive D, which rotates the shaft SH.
  • the shaft SH extends along a machine axis AX, which is the axis of rotation of the drive D at the same time.
  • a process fluid F is axially aspirated from the compressor CO and enters an overhang stage ST, is further compressed downstream by means of impellers IM, and enters a final stage LST for subsequent collection in the collection coil CC for entry into subsequent machine modules ,
  • 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, wherein the first shaft end SE1 is driven by the drive D and the second shaft end SE2 carries the overhang stage ST.
  • the invention means a portion of the shaft extending from the respective end of the shaft toward the shaft center, about one third of the total wavelength being referred to in the terminology of the invention as the shaft end.
  • the collecting spiral CC, the second radial bearing BE2 and a shaft seal SHS are arranged in the region of the first shaft end SE1, in addition to the torque-transmitting connection with the drive D.
  • the collecting spiral CC, the second radial bearing BE2 and a shaft seal SHS are arranged in the region of the first shaft end SE1, in addition to the torque-transmitting connection with the drive D.
  • the collecting spiral CC While the housing CC has a parting line in the extension of the machine axis AX, the collecting spiral CC is undivided in the extension of the machine axis or parallel thereto and is flanged to the housing C by means of first fastening elements SM1.
  • the collecting spiral CC carries the second radial bearing BE2 and the shaft seal SHS.
  • the undivided embodiment of the collecting spiral which is designed as a casting, has the advantage that it does not have any paragraph otherwise caused by a parting line in the circumferential direction, which could cause flow losses.
  • the attachment of the second radial bearing BE2 and the shaft seal SHS to the collecting spiral CC has the shortest possible tolerance chain between the radial bearing B2 and the shaft seal SHS result so that necessary for example thermal expansions radial clearances of the shaft SH in the shaft seal SHS can be minimal. In this way, a particularly good efficiency can be achieved.

Landscapes

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

Claims (2)

  1. Compresseur (CO) centrifruge pour comprimer un fluide (F) comportant :
    - un corps (C) qui a un plan (SP) de joint s'étendant parallèlement à un axe (AX) de machine ou suivant cet axe (AX),
    - un arbre (SH) qui s'étend suivant l'axe (AX) de machine et qui a un premier bout (SE1) d'arbre et un second bout (SE2) d'arbre,
    - au moins une roue (IM) qui est montée sur l'arbre (SH),
    - une volute (CC) collectrice qui est disposée en aval de la au moins une roue (IM) et qui collecte le fluide (F) comprimé avant une sortie dans un module de machine venant ensuite, la volute (CC) collectrice étant montée sur le premier bout (SE1) d'arbre,
    - un entraînement (D) qui est monté sur le premier bout (SE1) d'arbre,
    - dans lequel il est prévu sur l'arbre (SH) sur le deuxième bout (SE2) d'arbre une aspiration axiale sur un étage (ST) en surplomb du compresseur (CO) centrifuge.
    caractérisé
    en ce que la volute (CC) collectrice est constituée non divisée dans la direction périphérique et est bridée au corps (C) du compresseur (CO) centrifuge.
  2. Compresseur (CO) centrifuge suivant la revendication 1, dans lequel la volute (CC) collectrice est constituée sous la forme d'un support d'un palier (BE2) radial de support de l'arbre (SH).
EP11721272.0A 2010-05-18 2011-05-12 Compresseur centrifuge Not-in-force EP2572108B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102010020891 2010-05-18
PCT/EP2011/057660 WO2011144515A1 (fr) 2010-05-18 2011-05-12 Compresseur centrifuge

Publications (2)

Publication Number Publication Date
EP2572108A1 EP2572108A1 (fr) 2013-03-27
EP2572108B1 true EP2572108B1 (fr) 2015-08-26

Family

ID=44312333

Family Applications (1)

Application Number Title Priority Date Filing Date
EP11721272.0A Not-in-force EP2572108B1 (fr) 2010-05-18 2011-05-12 Compresseur centrifuge

Country Status (4)

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

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
KR101709998B1 (ko) 2011-12-06 2017-02-24 캐논 가부시끼가이샤 감광체 드럼 유닛
US9689502B2 (en) 2015-10-26 2017-06-27 Rolls-Royce Corporation Rotary exhaust valve system

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE503754C (de) * 1928-04-11 1930-07-26 Siemens Schuckertwerke Akt Ges Kreiselverdichter mit Gehaeusekuehlung
US2476191A (en) * 1945-06-15 1949-07-12 Westinghouse Electric Corp Multistage, axial flow, gas compressor

Family Cites Families (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2578617A (en) * 1946-11-15 1951-12-11 Worthington Pump & Mach Corp Multistage centrifugal compressor
DE835341C (de) * 1948-11-28 1952-03-31 Diederich Storjohann Kochtopfhandgriff
CH676487A5 (fr) * 1988-10-19 1991-01-31 Proizv Ob Nevsky Z Im V I
JP3799121B2 (ja) * 1997-03-19 2006-07-19 株式会社 日立インダストリイズ ２段遠心圧縮機
ID29972A (id) * 1999-01-25 2001-10-25 Elliott Turbo Rancangan selongsong untuk permesinan yang berputar dan metode untuk pembuatannya
US6345503B1 (en) * 2000-09-21 2002-02-12 Caterpillar Inc. Multi-stage compressor in a turbocharger and method of configuring same
GB2400631B (en) * 2003-04-16 2006-07-05 Adrian Alexander Hubbard Compound centrifugal and screw compressor
EP2050968A1 (fr) * 2007-10-19 2009-04-22 Siemens Aktiengesellschaft Récipient sous pression doté d'un couvercle
US8292576B2 (en) * 2008-03-31 2012-10-23 Honeywell International Inc. Compressor scrolls for auxiliary power units
DE102008057472B4 (de) * 2008-11-14 2011-07-14 Atlas Copco Energas GmbH, 50999 Mehrstufiger Radial-Turboverdichter

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE503754C (de) * 1928-04-11 1930-07-26 Siemens Schuckertwerke Akt Ges Kreiselverdichter mit Gehaeusekuehlung
US2476191A (en) * 1945-06-15 1949-07-12 Westinghouse Electric Corp Multistage, axial flow, gas compressor

Also Published As

Publication number Publication date
CN102893033B (zh) 2015-06-03
CN102893033A (zh) 2013-01-23
EP2572108A1 (fr) 2013-03-27
US20130064659A1 (en) 2013-03-14
WO2011144515A1 (fr) 2011-11-24

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