EP2955387A1 - Compresseur centrifuge - Google Patents

Compresseur centrifuge Download PDF

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Publication number
EP2955387A1
EP2955387A1 EP13874463.6A EP13874463A EP2955387A1 EP 2955387 A1 EP2955387 A1 EP 2955387A1 EP 13874463 A EP13874463 A EP 13874463A EP 2955387 A1 EP2955387 A1 EP 2955387A1
Authority
EP
European Patent Office
Prior art keywords
flow channel
fluid
impeller
outlet
opening section
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.)
Withdrawn
Application number
EP13874463.6A
Other languages
German (de)
English (en)
Other versions
EP2955387A4 (fr
Inventor
Shuichi Yamashita
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.)
Mitsubishi Heavy Industries Ltd
Mitsubishi Heavy Industries Compressor Corp
Original Assignee
Mitsubishi Heavy Industries Ltd
Mitsubishi Heavy Industries Compressor Corp
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 Mitsubishi Heavy Industries Ltd, Mitsubishi Heavy Industries Compressor Corp filed Critical Mitsubishi Heavy Industries Ltd
Publication of EP2955387A1 publication Critical patent/EP2955387A1/fr
Publication of EP2955387A4 publication Critical patent/EP2955387A4/fr
Withdrawn legal-status Critical Current

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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 configured to compress a gas using a centrifugal force.
  • a centrifugal compressor is configured to allow a gas to pass through a rotating impeller in a radial direction and compress the gas using a centrifugal force generated thereupon.
  • a multi-stage type centrifugal compressor including impellers in an axial direction in a plurality of stages and configured to compress a gas in a stepped manner is known.
  • the impeller In the centrifugal compressor, the impeller is rotatably supported on a rotary shaft in a casing, and as the impeller is rotated, a fluid such as an air, a gas, or the like, is suctioned from a suction port of the casing and a centrifugal force is applied thereto. Then, kinetic energy is converted into pressure energy by a diffuser and a scroll section to be delivered from a discharge port of the casing.
  • a fluid such as an air, a gas, or the like
  • a diffuser width is set to be smaller than in the related art, or a circulation flow channel that connects an impeller back surface and a diffuser inlet is installed (for example, see Patent Literature 1 and Patent Literature 2).
  • a structure in which the rotating stall cannot be easily generated is provided by increasing a flow velocity in a diffuser inlet and further reducing the flow angle of the flow in a radial direction.
  • a leakage from a seal (for example, a labyrinth seal) installed between a rotary shaft and a hub casing may be increased.
  • An object of the present invention is to provide a centrifugal compressor capable of more securely limiting the occurrence of rotating stall by increasing the flow velocity of a fluid that flows through an outlet flow channel.
  • a centrifugal compressor includes: an impeller configured to discharge a fluid introduced toward one side in an axial direction from an outlet directed to the outside in a radial direction through rotation thereof; and a casing installed to surround the impeller and having an outlet flow channel through which a fluid sent from the outlet of the impeller flows downstream thereby increasing the pressure of the fluid therein further downstream in the flow direction, wherein a circulation flow channel having a first opening section connected to the outlet flow channel and a second opening section connected to an upstream side of the first opening section in the outlet flow channel is formed.
  • the second opening section may be oriented toward the downstream side of the outlet flow channel.
  • the outlet flow channel may include: a diffuser connected to the outlet of the impeller and configured to convert kinetic energy applied to the fluid by the impeller into pressure energy, and a scroll connected to an outlet of the diffuser and configured to eject the fluid to the outside, and the first opening section may be formed at the scroll.
  • the outlet flow channel may include a diffuser connected to the outlet of the impeller and configured to convert kinetic energy applied to the fluid by the impeller into pressure energy, and the first opening section may be formed at an outlet side of the diffuser.
  • a centrifugal compressor 1 of the embodiment is generally constituted by a rotary shaft 2 rotatable about an axis O, an impeller 3 attached to the rotary shaft 2 and configured to compress a fluid G such as an air or the like using a centrifugal force, and a casing 5 configured to rotatably support the rotary shaft 2 and having a flow channel 4 through which the fluid G flows from an upstream side toward a downstream side.
  • the casing 5 is configured to form a substantially columnar contour, and the rotary shaft is disposed to pass through a center of the casing 5.
  • journal bearings 7 are installed at both ends of the rotary shaft 2 in the axial direction, and a thrust bearing 8 is installed at one end thereof.
  • the journal bearings 7 and the thrust bearing 8 rotatably support the rotary shaft 2. That is, the rotary shaft 2 is supported by the casing 5 via the journal bearings 7 and the thrust bearing 8.
  • a suction port 9 configured to introduce the fluid G from the outside is formed at one end side of the casing 5 in the axial direction and a discharge port 10 configured to discharge the fluid G to the outside is formed at the other end side.
  • an internal space 11 in communication with the suction port 9 and the discharge port 10 and having a diameter which is repeatedly increased and a decreased is provided.
  • the internal space 11 functions as a space for accommodating the impeller 3 and also functions as the above-mentioned flow channel 4. That is, the suction port 9 and the discharge port 10 are in communication with each other via the impeller 3 and the flow channel 4.
  • the casing 5 is constituted by a shroud casing 5a and a hub casing 5b, and the internal space 11 is defined by the shroud casing 5a and the hub casing 5b.
  • each of the impellers 3 is constituted by a substantially disk-shaped hub 13 having a diameter gradually increased toward the discharge port 10, a plurality of blades 14 radially attached to the hub 13 and disposed in a circumferential direction in parallel, and a shroud 15 attached to cover front end sides of the plurality of blades 14 in the circumferential direction.
  • the flow channel 4 is formed to advance in the axial direction and connect the impellers 3 while meandering in the radial direction of the rotary shaft 2 such that the fluid G is compressed by the plurality of impellers 3 in the stepped manner.
  • the flow channel 4 is generally 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 configured to convert kinetic energy applied to the fluid by the impellers 3 into pressure energy.
  • the suction passage 17 is a passage configured to convert the direction of the fluid G into the axial direction of the rotary shaft 2 immediately before the impeller 3 after the fluid G flows from the outside in the radial direction toward the inside in the radial direction.
  • the suction passage 17 is constituted by a straight passage 21 having a linear shape through which the fluid G flows from the outside in the radial direction toward the inside in the radial direction, and a corner passage 22 having a curved shape and configured to convert the flow direction of the fluid G flowing from the straight passage 21 from the inside in the radial direction into the axial direction to direct the fluid G toward the impeller 3.
  • a plurality of return vanes 23 radially disposed about the axis O and configured to divide the straight passage 21 in the circumferential direction of the rotary shaft 2 are installed at the straight passage 21 disposed between the two impellers 3.
  • the compression passage 18 is a passage configured to compress the fluid G conveyed from the suction passage 17, in the impeller 3, and is defined by being surrounded by a blade attachment surface of the hub 13 and an inner wall surface of the shroud 15.
  • the diffuser passage 19 has an inside in the radial direction in communication with the compression passage 18, and functions to allow the fluid G compressed by the impeller 3 to flow outward in the radial direction. Further, while the outside in the radial direction of the diffuser passage 19 is in communication with the return passage 20, the diffuser passage 19 connected to the outside in the radial direction of the impeller 3 disposed at the most downstream side of the flow channel 4 (in Fig. 1 , the sixth impeller 3) is in communication with an ejection scroll 12, which will be described below.
  • the return passage 20 is formed with a substantially U-shaped cross section, an upstream end side of the return passage 20 is in communication with the diffuser passage 19, and a downstream end side is in communication with the straight passage 21 of the suction passage 17.
  • the return passage 20 reverses the flow direction of the fluid G flowing to the outside in the radial direction through the diffuser passage 19 toward the inside in the radial direction due to the impeller 3 (the impeller 3 of the upstream side), and delivers the fluid G to the straight passage 21.
  • the ejection scroll 12 configured to eject the fluid from the ejection port is formed in the casing 5.
  • the ejection scroll 12 has a scroll flow channel 25 formed to surround the entire circumference of the outlet of the diffuser passage 19 disposed at an outer circumferential section of the impeller 3 of the final stage.
  • the scroll flow channel 25 is formed to surround the entire circumference of the outlet of the diffuser passage 19 disposed at the outer circumferential section of the impeller 3 of the final stage, and is formed to gradually and continuously enlarge a cross-sectional area thereof in a rotational direction of the impeller 3.
  • the diffuser passage 19 and the ejection scroll 12 function as an outlet flow channel 6 configured to increase a pressure of the fluid as the fluid is directed toward the downstream side while the fluid provided from the outlet of the impeller 3 flows therethrough.
  • a circulation flow channel 26 connecting the bottom surface of the scroll flow channel 25 of the ejection scroll 12 and the diffuser passage 19 is formed.
  • the circulation flow channel 26 is the flow channel 4 having a second opening section 28 formed in the vicinity of an inlet of the diffuser passage 19, and a first opening section 27 formed at the bottom surface of the scroll flow channel 25.
  • the second opening section 28 is formed to be directed toward the downstream side of the diffuser passage 19. That is, the second opening section 28 oriented such that the compressed air introduced from the first opening section 27 and ejected from the second opening section 28 is ejected toward the outlet of the diffuser passage 19.
  • the fluid G is compressed by the impellers 3 in the middle of flowing through the flow channel 4 in the above-mentioned sequence. That is, in the centrifugal compressor 1, the fluid G is compressed by the plurality of impellers 3 in the stepped manner, and thus, a large compression ratio can be easily obtained.
  • the circulation flow channel 26 is configured to capture some of the compressed fluid from the first opening section 27 and eject the compressed fluid from the second opening section 28 such that some of the compressed fluid is circulated between the diffuser passage 19 and the ejection scroll 12.
  • the compressed air is introduced from the first opening section 27 of the scroll flow channel 25 to be ejected from the second opening section 28 of the diffuser passage 19 via the circulation flow channel 26. That is, the compressed air is circulated to increase a flow velocity of the fluid flowing through the diffuser passage 19 with the compressed fluid. Accordingly, occurrences of rotating stall can be more securely limited.
  • the second opening section 28 is formed to be oriented toward the downstream side of the diffuser passage 19, since the compressed fluid introduced from the second opening section 28 is ejected toward the downstream side of the diffuser passage 19, the flow velocity of the fluid flowing through the diffuser passage 19 can be further increased.
  • a formed place of the first opening section 27 may be a downstream side of the second opening section 28 on the outlet flow channel constituted by the diffuser passage 19 and the ejection scroll 12.
  • a configuration in which the first opening section 27 is formed at the outlet side of the diffuser passage 19 may be provided.
  • the circulation flow channel 26 may be branched off from a conventional line to eject the fluid to the diffuser passage 19 without necessity of newly forming the entire circulation flow channel.
  • the second opening section 28 is configured to be oriented toward a slipstream side of the diffuser passage 19, it is not limited thereto as long the flow velocity of the compressed fluid flowing through the diffuser passage 19 should not decreased.
  • the fluid may be injected in a direction perpendicular to the extending direction of the diffuser passage 19.
  • occurrences of rotating stall can be more securely limited by circulating the fluid such that the fluid introduced from the second opening section of the outlet flow channel increases the flow velocity of the fluid flowing through the outlet flow channel.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
EP13874463.6A 2013-02-05 2013-09-27 Compresseur centrifuge Withdrawn EP2955387A4 (fr)

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
PCT/JP2013/076373 WO2014122819A1 (fr) 2013-02-05 2013-09-27 Compresseur centrifuge

Publications (2)

Publication Number Publication Date
EP2955387A1 true EP2955387A1 (fr) 2015-12-16
EP2955387A4 EP2955387A4 (fr) 2016-09-07

Family

ID=51299428

Family Applications (1)

Application Number Title Priority Date Filing Date
EP13874463.6A Withdrawn EP2955387A4 (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

Family Cites Families (15)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1403519A1 (de) * 1961-06-24 1969-12-11 Gutehoffnungshuette Sterkrade Einrichtung zur Grenzschichtabsaugung bei Turbomaschinen,insbesondere Radialverdichtern
JPS4847605A (fr) * 1971-10-19 1973-07-06
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
JP2005240680A (ja) * 2004-02-26 2005-09-08 Mitsubishi Heavy Ind Ltd 遠心圧縮機
US8122724B2 (en) * 2004-08-31 2012-02-28 Honeywell International, Inc. Compressor including an aerodynamically variable diffuser
JP4655603B2 (ja) * 2004-12-01 2011-03-23 株式会社豊田自動織機 遠心圧縮機
EP1710442A1 (fr) * 2005-04-04 2006-10-11 ABB Turbo Systems AG Système de stabilisation de courant pour compresseur radial
JP5031012B2 (ja) 2006-07-13 2012-09-19 三菱重工業株式会社 圧縮機およびその運転制御方法
JP2010151032A (ja) * 2008-12-25 2010-07-08 Ihi Corp 遠心圧縮機
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
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
JP2011122516A (ja) 2009-12-10 2011-06-23 Mitsubishi Heavy Ind Ltd 遠心圧縮機
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

Also Published As

Publication number Publication date
US20150354588A1 (en) 2015-12-10
WO2014122819A1 (fr) 2014-08-14
CN104822948A (zh) 2015-08-05
JP2014152637A (ja) 2014-08-25
EP2955387A4 (fr) 2016-09-07

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