WO2014122819A1 - Compresseur centrifuge - Google Patents

Compresseur centrifuge Download PDF

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Publication number
WO2014122819A1
WO2014122819A1 PCT/JP2013/076373 JP2013076373W WO2014122819A1 WO 2014122819 A1 WO2014122819 A1 WO 2014122819A1 JP 2013076373 W JP2013076373 W JP 2013076373W WO 2014122819 A1 WO2014122819 A1 WO 2014122819A1
Authority
WO
WIPO (PCT)
Prior art keywords
impeller
fluid
outlet
opening
passage
Prior art date
Application number
PCT/JP2013/076373
Other languages
English (en)
Japanese (ja)
Inventor
山下　修一
Original Assignee
三菱重工業株式会社
三菱重工コンプレッサ株式会社
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 三菱重工業株式会社, 三菱重工コンプレッサ株式会社 filed Critical 三菱重工業株式会社
Priority to EP13874463.6A priority Critical patent/EP2955387A4/fr
Priority to CN201380062485.0A priority patent/CN104822948A/zh
Priority to US14/759,373 priority patent/US20150354588A1/en
Publication of WO2014122819A1 publication Critical patent/WO2014122819A1/fr

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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
    • F04D29/66—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
    • 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
    • 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
    • F04D29/08—Sealings
    • F04D29/10—Shaft sealings
    • F04D29/102—Shaft 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
    • 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
    • F04D29/4206—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
    • 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
    • F04D29/684—Combating cavitation, whirls, noise, vibration or the like; Balancing by influencing boundary layers especially adapted for elastic fluid pumps by fluid injection
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
    • F05D2250/00—Geometry
    • F05D2250/50—Inlet or outlet
    • F05D2250/52—Outlet

Definitions

  • the present invention relates to a centrifugal compressor that compresses gas using centrifugal force.
  • a centrifugal compressor passes gas in the radial direction of a rotating impeller and compresses the gas by using centrifugal force generated at that time.
  • a multistage centrifugal compressor that includes multiple stages of impellers in the axial direction and compresses gas in stages.
  • an impeller In the centrifugal compressor, an impeller is rotatably supported on a rotating shaft in a casing, and by rotating the impeller, a fluid such as air or gas is sucked from a suction port of the casing to apply a centrifugal force. . And the kinetic energy is converted into pressure energy by a diffuser and a scroll part, and it sends out from the discharge port of a casing.
  • the width of the diffuser is made narrower than usual or the circulation connecting the impeller back surface and the diffuser inlet is performed.
  • a flow path may be installed (for example, refer to Patent Document 1 and Patent Document 2). In either configuration, the flow velocity at the inlet of the diffuser is increased, and the flow is directed in a more radial direction to reduce the flow angle.
  • An object of the present invention is to provide a centrifugal compressor that can more reliably suppress the rotating stall by increasing the flow velocity of the fluid flowing through the outlet channel.
  • the centrifugal compressor is provided so as to surround the impeller, which rotates to feed the fluid flowing in toward the one side in the axial direction from the outlet facing the radially outer side.
  • a casing formed with an outlet flow path for increasing the pressure of the fluid as it goes downstream while flowing the fluid sent out from the outlet of the impeller, and connected to the outlet flow path
  • a circulation channel having an opening and a second opening connected to the upstream side of the first opening in the outlet channel is formed.
  • the turning stall can be more reliably suppressed by circulating the fluid flowing in from the second opening of the outlet channel so as to increase the flow velocity of the fluid flowing through the outlet channel.
  • the second opening may be configured to be directed downstream of the outlet channel.
  • the flow velocity of the fluid flowing through the outlet channel can be further increased.
  • the outlet channel is connected to an outlet of the impeller, is connected to a diffuser that converts kinetic energy given to the fluid by the impeller into pressure energy, and is connected to an outlet of the diffuser.
  • the first opening may be provided in the scroll.
  • the outlet channel is connected to an outlet of the impeller and includes a diffuser that converts kinetic energy given to the fluid by the impeller into pressure energy, and the first opening includes It is good also as a structure provided in the exit side of the diffuser.
  • the fluid stalled from the second opening of the outlet channel is circulated so as to increase the flow velocity of the fluid flowing through the outlet channel, whereby the turning stall can be more reliably suppressed.
  • centrifugal compressor of embodiment of this invention It is a schematic sectional drawing of the centrifugal compressor of embodiment of this invention. It is the figure which expanded the impeller and scroll part of the last stage in the centrifugal compressor of the embodiment of the present invention. It is the figure which expanded the impeller and scroll part of the last stage in the centrifugal compressor of the modification of embodiment of this invention.
  • the centrifugal compressor 1 of the present embodiment mainly includes a rotating shaft 2 that is rotated around an axis O, and a fluid G such as air that is attached to the rotating shaft 2 and uses centrifugal force.
  • the impeller 3 to be compressed, and a casing 5 in which a flow path 4 for flowing the fluid G from the upstream side to the downstream side is formed while the rotary shaft 2 is rotatably supported.
  • the casing 5 is formed so as to form a substantially cylindrical outline, and the rotary shaft 2 is disposed so as to penetrate the center.
  • Journal bearings 7 are provided at both ends of the casing 5 in the axial direction of the rotary shaft 2, and thrust bearings 8 are provided at one end.
  • the journal bearing 7 and the thrust bearing 8 support the rotary shaft 2 in a rotatable manner. That is, the rotary shaft 2 is supported by the casing 5 via the journal bearing 7 and the thrust bearing 8.
  • a suction port 9 through which the fluid G flows from the outside is provided on one end side in the axial direction of the casing 5, and a discharge port 10 through which the fluid G flows out to the outside is provided at the other end side.
  • an internal space 11 that communicates with the suction port 9 and the discharge port 10 and repeats the diameter reduction and the diameter expansion.
  • the internal space 11 functions as a space for accommodating the impeller 3 and also functions as the flow path 4 described above. That is, the suction port 9 and the discharge port 10 communicate with each other through the impeller 3 and the flow path 4.
  • the casing 5 is comprised by the shroud casing 5a and the hub casing 5b, and the internal space 11 is formed of the shroud casing 5a and the hub casing 5b.
  • a plurality of impellers 3 are arranged at intervals in the axial direction of the rotary shaft 2.
  • six impellers 3 are provided, but it is sufficient that at least one impeller 3 is provided.
  • each impeller 3 includes a substantially disk-shaped hub 13 that gradually increases in diameter as it advances toward the discharge port 10, and a plurality of blades 14 that are radially attached to the hub 13 and arranged in the circumferential direction.
  • the shroud 15 is attached so as to cover the distal ends of the plurality of blades 14 in the circumferential direction.
  • the flow path 4 is formed so as to advance in the axial direction while meandering in the radial direction of the rotary shaft 2 so that the fluid G is compressed stepwise by the plurality of impellers 3 and to connect the impellers 3 to each other.
  • the flow path 4 is mainly constituted by a suction passage 17, a compression passage 18, a diffuser passage 19, and a return passage 20.
  • the diffuser passage 19 is a passage that converts kinetic energy given to the fluid by the impeller 3 into pressure energy.
  • the suction passage 17 is a passage that changes the direction of the fluid G to the axial direction of the rotary shaft 2 immediately before the impeller 3 after flowing the fluid G from the radially outer side to the radially inner side. Specifically, the straight straight passage 21 for flowing the fluid G from the radially outer side toward the radially inner side, and the flow direction of the fluid G flowing from the straight passage 21 from the radially inner side to the axial direction. And a curved corner passage 22 that converts the fluid G toward the impeller 3.
  • the straight passage 21 positioned between the two impellers 3 is provided with a plurality of return vanes 23 that are arranged radially about the axis O and divide the straight passage 21 in the circumferential direction of the rotary shaft 2. .
  • the compression passage 18 is a passage for compressing the fluid G sent from the suction passage 17 in the impeller 3, and is defined by being surrounded by the blade mounting surface of the hub 13 and the inner wall surface of the shroud 15. Yes.
  • the diffuser passage 19 has a radially inner side communicating with the compression passage 18 and plays a role of flowing the fluid G compressed by the impeller 3 outward in the radial direction.
  • the radially outer side of the diffuser passage 19 communicates with the return passage 20, but the diameter of the impeller 3 (sixth stage impeller 3 in FIG. 1) located on the most downstream side of the flow path 4.
  • a diffuser passage 19 that extends outward in the direction communicates with a discharge scroll 12 described later.
  • the return passage 20 has a substantially U-shaped cross section, the upstream end side of the return passage 20 communicates with the diffuser passage 19, and the downstream end side communicates with the straight passage 21 of the suction passage 17.
  • the return passage 20 reverses the flow direction of the fluid G that has flowed radially outward through the diffuser passage 19 by the impeller 3 (upstream impeller 3) to the inside in the radial direction, and sends it to the straight passage 21. ing.
  • a discharge scroll 12 for discharging fluid from the discharge port is provided in the casing 5.
  • the discharge scroll 12 has a scroll passage 25 formed so as to surround the entire periphery of the outlet of the diffuser passage 19 located at the outer peripheral portion of the impeller 3 at the final stage.
  • the scroll flow path 25 is formed so as to surround the entire circumference of the outlet of the diffuser passage 19 located at the outer peripheral portion of the impeller 3 at the final stage, and its cross-sectional area gradually increases along the rotation direction of the impeller 3. It is formed to do.
  • the diffuser passage 19 and the discharge scroll 12 function as an outlet flow path 6 through which the fluid fed from the outlet of the impeller 3 flows and increases the pressure of the fluid toward the downstream side.
  • the circulation flow path 26 which connects the bottom face of the scroll flow path 25 of the discharge scroll 12 and the diffuser passage 19 is provided.
  • the circulation channel 26 is a channel 4 having a second opening 28 provided near the inlet of the diffuser passage 19 and a first opening 27 provided on the bottom surface of the scroll channel 25. is there.
  • the second opening 28 is formed to face the downstream side of the diffuser passage 19. That is, the compressed air flowing in from the first opening 27 and ejected from the second opening 28 is directed so as to be ejected toward the outlet side of the diffuser passage 19.
  • the fluid G is compressed by each impeller 3 while flowing through the flow path 4 in the order described above.
  • the fluid G is compressed in stages by the plurality of impellers 3, whereby a large compression ratio can be easily obtained.
  • the circulation channel 26 takes in a part of the compressed fluid from the first opening 27 and ejects it from the second opening 28 to circulate a part of the compressed fluid between the diffuser passage 19 and the discharge scroll 12. It is configured to be.
  • the compressed air flows from the first opening 27 of the scroll flow path 25 and is ejected from the second opening 28 of the diffuser passage 19 through the circulation flow path 26. That is, the compressed air circulates so as to increase the flow velocity of the fluid flowing through the compressed fluid diffuser passage 19. Thereby, turning stall can be suppressed more reliably.
  • the second opening 28 is formed so as to be directed downstream of the diffuser passage 19, the compressed fluid introduced from the second opening 28 is ejected toward the downstream side of the diffuser passage 19. Therefore, the flow velocity of the fluid flowing through the diffuser passage 19 can be further increased.
  • the pressure difference between the first opening 27 and the second opening 28 can be increased, so that the circulating flow can flow more reliably. be able to.
  • compressed air is not introduced into the back surface of the impeller 3, for example, when a seal such as a labyrinth seal is provided between the rotary shaft 2 and the casing 5, leakage from the seal increases. There is no.
  • the first opening 27 of the circulation channel 26 is provided in the discharge scroll 12.
  • the first opening 27 is formed by the diffuser passage 19 and the discharge scroll 12. It may be on the outlet channel and downstream of the second opening 28.
  • the first opening 27 may be provided on the outlet side of the diffuser passage 19.
  • the technical scope of the present invention is not limited to the above embodiment, and various modifications can be made without departing from the spirit of the present invention.
  • the second opening 28 is configured to face the downstream side of the diffuser passage 19, but the present invention is not limited to this, and the flow rate of the compressed fluid flowing through the diffuser passage 19 must be reduced. That's fine. For example, you may inject in the direction orthogonal to the extension direction of the diffuser channel
  • the rotation stall can be more reliably suppressed by circulating the fluid flowing in from the second opening of the outlet channel so as to increase the flow rate of the fluid flowing through the outlet channel.

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

Abstract

L'invention concerne un compresseur centrifuge pourvu : d'un rouet (3) dans lequel un fluide qui entre en s'écoulant vers un côté dans la direction d'arbre est évacué par rotation depuis un refoulement qui est en regard vers l'extérieur dans la direction radiale ; et d'un carter (5) disposé autour du rouet (3), et dans lequel est formé un canal d'écoulement de refoulement (6) pour faire circuler le fluide évacué depuis le refoulement du rouet (3) et augmenter la pression du fluide à mesure que le fluide s'écoule davantage vers l'aval. Dans le compresseur centrifuge est formé un canal d'écoulement de circulation (26) ayant une première section d'ouverture (28) raccordée au canal d'écoulement de refoulement (6) et une seconde section d'ouverture (27) raccordée au canal d'écoulement de refoulement (6) davantage en amont de la première section d'ouverture (28).
PCT/JP2013/076373 2013-02-05 2013-09-27 Compresseur centrifuge WO2014122819A1 (fr)

Priority Applications (3)

Application Number Priority Date Filing Date Title
EP13874463.6A EP2955387A4 (fr) 2013-02-05 2013-09-27 Compresseur centrifuge
CN201380062485.0A CN104822948A (zh) 2013-02-05 2013-09-27 离心式压缩机
US14/759,373 US20150354588A1 (en) 2013-02-05 2013-09-27 Centrifugal compressor

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2013020704A JP2014152637A (ja) 2013-02-05 2013-02-05 遠心圧縮機
JP2013-020704 2013-02-05

Publications (1)

Publication Number Publication Date
WO2014122819A1 true WO2014122819A1 (fr) 2014-08-14

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Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/JP2013/076373 WO2014122819A1 (fr) 2013-02-05 2013-09-27 Compresseur centrifuge

Country Status (5)

Country Link
US (1) US20150354588A1 (fr)
EP (1) EP2955387A4 (fr)
JP (1) JP2014152637A (fr)
CN (1) CN104822948A (fr)
WO (1) WO2014122819A1 (fr)

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US9618013B2 (en) * 2013-07-17 2017-04-11 Rotational Trompe Compressors, Llc Centrifugal gas compressor method and system
JP6184018B2 (ja) * 2014-02-06 2017-08-23 三菱重工業株式会社 中間吸込型ダイアフラムおよび遠心回転機械
JP6642189B2 (ja) * 2016-03-29 2020-02-05 三菱重工コンプレッサ株式会社 遠心圧縮機
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
KR102545557B1 (ko) * 2018-06-12 2023-06-21 엘지전자 주식회사 원심 압축기

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS4847605A (fr) * 1971-10-19 1973-07-06
JP2005240680A (ja) * 2004-02-26 2005-09-08 Mitsubishi Heavy Ind Ltd 遠心圧縮機
JP2006152972A (ja) * 2004-12-01 2006-06-15 Toyota Industries Corp 遠心圧縮機
JP2010043648A (ja) 2006-07-13 2010-02-25 Mitsubishi Heavy Ind Ltd 圧縮機およびその運転制御方法
JP2011122516A (ja) 2009-12-10 2011-06-23 Mitsubishi Heavy Ind Ltd 遠心圧縮機

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DE1403519A1 (de) * 1961-06-24 1969-12-11 Gutehoffnungshuette Sterkrade Einrichtung zur Grenzschichtabsaugung bei Turbomaschinen,insbesondere Radialverdichtern
US4131389A (en) * 1975-11-28 1978-12-26 The Garrett Corporation Centrifugal compressor with improved range
US4695224A (en) * 1982-01-04 1987-09-22 General Electric Company Centrifugal compressor with injection of a vaporizable liquid
US8122724B2 (en) * 2004-08-31 2012-02-28 Honeywell International, Inc. Compressor including an aerodynamically variable diffuser
EP1710442A1 (fr) * 2005-04-04 2006-10-11 ABB Turbo Systems AG Système de stabilisation de courant pour compresseur radial
JP2010151031A (ja) * 2008-12-25 2010-07-08 Ihi Corp 遠心圧縮機
JP2010151033A (ja) * 2008-12-25 2010-07-08 Ihi Corp 遠心圧縮機
JP2010151032A (ja) * 2008-12-25 2010-07-08 Ihi Corp 遠心圧縮機
JP5479021B2 (ja) * 2009-10-16 2014-04-23 三菱重工業株式会社 排気ターボ過給機のコンプレッサ
FR2958967B1 (fr) * 2010-04-14 2013-03-15 Turbomeca Procede d'adaptation de debit d'air de turbomachine a compresseur centrifuge et diffuseur de mise en oeuvre

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS4847605A (fr) * 1971-10-19 1973-07-06
JP2005240680A (ja) * 2004-02-26 2005-09-08 Mitsubishi Heavy Ind Ltd 遠心圧縮機
JP2006152972A (ja) * 2004-12-01 2006-06-15 Toyota Industries Corp 遠心圧縮機
JP2010043648A (ja) 2006-07-13 2010-02-25 Mitsubishi Heavy Ind Ltd 圧縮機およびその運転制御方法
JP2011122516A (ja) 2009-12-10 2011-06-23 Mitsubishi Heavy Ind Ltd 遠心圧縮機

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See also references of EP2955387A4 *

Also Published As

Publication number Publication date
JP2014152637A (ja) 2014-08-25
EP2955387A1 (fr) 2015-12-16
CN104822948A (zh) 2015-08-05
EP2955387A4 (fr) 2016-09-07
US20150354588A1 (en) 2015-12-10

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