EP0961034B1 - Compresseur radial - Google Patents

Compresseur radial Download PDF

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Publication number
EP0961034B1
EP0961034B1 EP98810487A EP98810487A EP0961034B1 EP 0961034 B1 EP0961034 B1 EP 0961034B1 EP 98810487 A EP98810487 A EP 98810487A EP 98810487 A EP98810487 A EP 98810487A EP 0961034 B1 EP0961034 B1 EP 0961034B1
Authority
EP
European Patent Office
Prior art keywords
compressor
gap
region
separating gap
radially extending
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.)
Expired - Lifetime
Application number
EP98810487A
Other languages
German (de)
English (en)
Other versions
EP0961034A1 (fr
Inventor
Dirk Dr. Wunderwald
Joachim Bremer
Christian Dr. Müller
Mihajlo Dr. Bothien
Jürg Greber
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.)
Accelleron Industries AG
Original Assignee
ABB Turbo Systems 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 ABB Turbo Systems AG filed Critical ABB Turbo Systems AG
Priority to EP98810487A priority Critical patent/EP0961034B1/fr
Priority to DE59809488T priority patent/DE59809488D1/de
Priority to TW088108094A priority patent/TW562900B/zh
Priority to CZ19991778A priority patent/CZ291692B6/cs
Priority to KR10-1999-0018502A priority patent/KR100537036B1/ko
Priority to US09/316,964 priority patent/US6238179B1/en
Priority to CN99212341U priority patent/CN2381815Y/zh
Priority to CN99107042A priority patent/CN1102706C/zh
Priority to JP14544299A priority patent/JP4503726B2/ja
Publication of EP0961034A1 publication Critical patent/EP0961034A1/fr
Application granted granted Critical
Publication of EP0961034B1 publication Critical patent/EP0961034B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime 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
    • F04D17/00—Radial-flow pumps, e.g. centrifugal pumps; Helico-centrifugal pumps
    • F04D17/08—Centrifugal 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
    • F04D29/08—Sealings
    • F04D29/16—Sealings between pressure and suction sides
    • F04D29/161—Sealings between pressure and suction sides especially adapted for elastic fluid pumps
    • F04D29/162—Sealings between pressure and suction sides especially adapted for elastic fluid pumps of a centrifugal flow wheel
    • 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
    • F04D29/58—Cooling; Heating; Diminishing heat transfer
    • F04D29/582—Cooling; Heating; Diminishing heat transfer specially adapted for elastic fluid pumps
    • F04D29/5846—Cooling; Heating; Diminishing heat transfer specially adapted for elastic fluid pumps cooling by injection

Definitions

  • the invention relates to a radial compressor according to the preamble of the claim 1.
  • turbomachinery Seals especially labyrinth seals, are widely used.
  • fluid flow Separation gap between rotating and standing parts occurs as a result of forming flow boundary layers on a high friction. Thereby there is a heating of the fluid in the separation gap and thus also a heating the components surrounding the separation gap.
  • the high material temperatures have a reduction in the lifespan of the corresponding components Episode.
  • the gas divides and flows mainly radially inwards and outwards, through the individual sealing elements of the labyrinth seal. Especially the radial one partial flow directed towards the outside should also flow through the separation gap Prevent hot compressor air from escaping the compressor wheel.
  • the invention tries to avoid all these disadvantages. You have the task based on a radial compressor with a simplified, but in effect to provide improved cooling device.
  • this is achieved in that with a device according to the preamble of claim 1, the feed device for the gaseous Cooling medium upstream of the predominantly radially extending gap area of the separation gap opens into the latter.
  • This solution can be used for an additional annular space or additional feed spaces in the predominantly radially extending gap area of the separating gap to be dispensed with.
  • the cooling medium used can be mainly in the otherwise radially extending gap area of the separating gap penetrating hot Replace leakage air. This will attach to the back wall of the compressor wheel from the beginning, the flow boundary layer, above all through the supplied cooling medium formed. In particular, therefore, this can be particularly endangered area of the radial compressor an improved cooling effect be guaranteed.
  • the supply channel has several openings interrupted by recesses Guide webs, with the recesses simultaneously the feed channels for form the cooling medium.
  • the exhaust gas turbocharger shown only partially in FIG. 1 consists of a radial compressor 1 and an exhaust gas turbine, not shown, which in a Bearing housing 2 supported shaft 3 are interconnected.
  • the radial compressor 1 has a machine axis 4 lying in the shaft 3. He is with equipped with a compressor housing 5 in which a compressor wheel 6 rotates with the shaft 3 is connected.
  • the compressor wheel 6 has one with a variety of Blades 7 occupied hub 8. Between the hub 8 and the compressor housing 5, a flow channel 9 is formed. Downstream of the blades 7 connects to the flow channel 9 a radially arranged, bladed diffuser 10 on, which in turn opens into a spiral 11 of the radial compressor 1.
  • the Compressor housing 5 mainly consists of an air inlet housing 12, one Air outlet housing 13, a diffuser plate 14 and an intermediate wall 15 to the bearing housing 2.
  • the hub 8 has a rear wall 16 on the turbine side and a fastening sleeve 17 for the shaft 3, the latter and the fastening sleeve 17 together are connected.
  • the fastening sleeve 17 is of the intermediate wall 15 of the Compressor housing 5 added.
  • another suitable one Compressor wheel-shaft connection can be selected.
  • the use of a unspeaked diffuser possible.
  • a first gap area 19 runs parallel to the machine axis 4 and is with both the outlet of the compressor wheel 6 and one predominantly radial in the area of the rear wall 16 of the compressor wheel 6 extending, second gap region 20 connected.
  • the latter goes in between the fastening sleeve 17 and the intermediate wall 15 formed and third gap region 21 likewise running parallel to the machine axis 4 about.
  • Part of the predominantly radially extending second gap area 20 are an entry area adjoining the first gap area 19 22, a non-contact seal 23 designed as a labyrinth seal and an intermediate space 24 connected to the third gap region 21 in turn communicates with a drain line, not shown.
  • the diffuser plate 14 is provided with a Opening 28 is provided for receiving the feed line 26 and points radially at it inner end on a slot formed as a supply channel 25.
  • the supply channel 25 is with the entry area 22 of the second gap area 20 of the separation gap 18 arranged radially aligned.
  • the compressor wheel 6 When the exhaust gas turbocharger is operating, the compressor wheel 6 sucks as the working medium 29 ambient air, which via the flow channel 9 and the diffuser 10 in the spiral 11 arrives, compresses there and finally does not charge it shown, used with the exhaust gas turbocharger internal combustion engine becomes. Actuated on its way from the flow channel 9 to the diffuser 10 the ambient air 29 heated in the radial compressor 1 as a leakage flow 30 also the first gap region 19 and thus the separating gap 18. At the same time however, a gaseous cooling medium 31 into the second via the feed device 27 Gap area 20 of the separation gap 18 introduced. For example, this can be air from the outlet of the charge air cooler of the internal combustion engine, not shown. Of course, both the use of other cooling media as well as an external supply of the cooling medium possible.
  • the cooling medium 31 replaces the hot leakage flow 30, so that the the rear wall 16 of the compressor wheel 6 already forming boundary layer At the beginning, it is primarily formed by the supplied cooling medium 31. Since that Cooling medium 31 only flows radially inwards, it is possible on the one hand to achieve a significantly improved cooling effect and on the other hand also Reduce friction losses. Finally, the cooling medium 31 becomes common with the leakage flow 30 of the working medium 29, across the gap 24 and via an attack in the intermediate wall 15 of the compressor housing 5, Discharge device 32, not shown, passed from the separation gap 18.
  • the diffuser plate 14 is in the region of the supply duct 25 with an intermediate ring receiving the feed line 26 33 provided (Fig. 2).
  • the intermediate ring 33 has several distributed over the circumference Guide webs 34, which of recesses formed as feed channels 35 be interrupted (Fig. 3).
  • the guide webs 34 are designed so that the feed channels 35 have an orientation in the direction of rotation of the compressor wheel 6 experienced. This leads to a so-called swirl injection of the cooling medium 31, which is the friction and thus the heating of the compressor wheel 6 significantly reduced.
  • this function can also be implemented be by the diffuser plate 14 in the region of the supply channel 25 accordingly is profiled (not shown).
  • a sealing element 36 is arranged in the separating gap 18 (FIG. 4). With the help of this sealing element 36, it is possible to control the pressure of the remaining Leakage flow 30 to reduce so far that the pressure of the inflowing Cooling medium 31 advantageously even under that at the outlet of the compressor wheel 6 prevailing pressure of the working medium 29 may lie. That way even with relatively small amounts of the cooling medium 31 effective cooling of the Compressor wheel 6 can be guaranteed.

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

Claims (6)

  1. Compresseur radial avec une roue de compresseur (6) disposée sur un arbre (3) et qui présente une paroi arrière (16) qui s'étend principalement dans le sens radial, un boítier de compresseur (5) qui entoure la roue de compresseur (6), un canal d'écoulement (9) pour un fluide de travail (29) du compresseur radial (1), qui est formé entre la roue de compresseur (6) et le boítier (5) du compresseur, ainsi qu'un interstice de séparation (18) relié au canal d'écoulement (9), entre la roue (6) du compresseur et le boítier (5) du compresseur, un dispositif d'amenée (27) d'un fluide de refroidissement gazeux (31) disposé dans le boítier (5) du compresseur et un dispositif d'évacuation (32) correspondant, le dispositif d'amenée (27) débouchant dans l'interstice de séparation (18) et l'interstice de séparation (18) présentant dans la région de la paroi arrière (16) de la roue (6) du compresseur une zone d'interstice (20) qui s'étend principalement dans le sens radial, caractérisé en ce que le dispositif d'amenée (27) débouche dans l'interstice de séparation en amont de la zone (20) de l'interstice de séparation (18) qui s'étend principalement dans le sens radial.
  2. Compresseur radial selon la revendication 1, caractérisé en ce que le dispositif d'amenée (27) présente un canal d'alimentation (25) et en ce que la zone (20) de l'interstice de séparation (18) qui s'étend principalement dans le sens radial présente une zone d'entrée (22), le canal d'alimentation (25) et la zone d'entrée (22) étant alignés l'un sur l'autre dans le sens radial.
  3. Compresseur radial selon la revendication 2, caractérisé en ce que plusieurs canaux d'amenée (35) orientés dans le sens de rotation de la roue (6) du compresseur sont disposés dans le canal d'alimentation (25).
  4. Compresseur radial selon la revendication 3, caractérisé en ce que plusieurs ailettes de guidage (34) interrompues par des découpes sont disposées dans le canal d'alimentation (25), les découpes formant les canaux d'amenée (35).
  5. Compresseur radial selon la revendication 4, caractérisé en ce qu'un élément d'étanchéité (36) est disposé dans l'interstice de séparation (18) en amont de la zone d'entrée (22) dans la zone (20) de l'interstice qui s'étend principalement dans le sens radial.
  6. Compresseur radial selon l'une des revendications 2 à 5, caractérisé en ce qu'un joint d'étanchéité sans contact (23) est disposé en aval de la zone d'entrée (22) dans la zone (20) de l'interstice de séparation (18) qui s'étend principalement dans le sens radial.
EP98810487A 1998-05-25 1998-05-25 Compresseur radial Expired - Lifetime EP0961034B1 (fr)

Priority Applications (9)

Application Number Priority Date Filing Date Title
EP98810487A EP0961034B1 (fr) 1998-05-25 1998-05-25 Compresseur radial
DE59809488T DE59809488D1 (de) 1998-05-25 1998-05-25 Radialverdichter
TW088108094A TW562900B (en) 1998-05-25 1999-05-18 Centrifugal compressor
CZ19991778A CZ291692B6 (cs) 1998-05-25 1999-05-19 Radiální kompresor
KR10-1999-0018502A KR100537036B1 (ko) 1998-05-25 1999-05-21 원심 압축기
US09/316,964 US6238179B1 (en) 1998-05-25 1999-05-24 Centrifugal compressor
CN99212341U CN2381815Y (zh) 1998-05-25 1999-05-25 涡轮压缩机
CN99107042A CN1102706C (zh) 1998-05-25 1999-05-25 涡轮压缩机
JP14544299A JP4503726B2 (ja) 1998-05-25 1999-05-25 遠心圧縮機

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP98810487A EP0961034B1 (fr) 1998-05-25 1998-05-25 Compresseur radial

Publications (2)

Publication Number Publication Date
EP0961034A1 EP0961034A1 (fr) 1999-12-01
EP0961034B1 true EP0961034B1 (fr) 2003-09-03

Family

ID=8236108

Family Applications (1)

Application Number Title Priority Date Filing Date
EP98810487A Expired - Lifetime EP0961034B1 (fr) 1998-05-25 1998-05-25 Compresseur radial

Country Status (8)

Country Link
US (1) US6238179B1 (fr)
EP (1) EP0961034B1 (fr)
JP (1) JP4503726B2 (fr)
KR (1) KR100537036B1 (fr)
CN (2) CN1102706C (fr)
CZ (1) CZ291692B6 (fr)
DE (1) DE59809488D1 (fr)
TW (1) TW562900B (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US11199201B2 (en) 2016-02-22 2021-12-14 Mitsubishi Heavy Industries Marine Machinery & Equipment Co., Ltd. Impeller back surface cooling structure and supercharger

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DE10325980A1 (de) * 2003-06-07 2004-12-23 Daimlerchrysler Ag Abgasturbolader
US7252474B2 (en) * 2003-09-12 2007-08-07 Mes International, Inc. Sealing arrangement in a compressor
US7234918B2 (en) * 2004-12-16 2007-06-26 Siemens Power Generation, Inc. Gap control system for turbine engines
DE102005018771B4 (de) * 2005-04-22 2015-06-18 Man Diesel & Turbo Se Brennkraftmaschine
CN101297118B (zh) * 2005-09-19 2011-09-28 英格索尔-兰德公司 用于离心压缩机的静止密封环
ES2357754T3 (es) * 2005-09-19 2011-04-29 Ingersoll Rand Company Impulsor para un compresor centrífugo.
EP1937979B1 (fr) * 2005-09-19 2010-06-23 Ingersoll-Rand Company Compresseur centrifuge comprenant un systeme de joints
US8556516B2 (en) * 2010-08-26 2013-10-15 Hamilton Sundstrand Corporation Compressor bearing cooling inlet plate
JP5700999B2 (ja) * 2010-10-06 2015-04-15 三菱重工業株式会社 遠心圧縮機
US8784048B2 (en) * 2010-12-21 2014-07-22 Hamilton Sundstrand Corporation Air cycle machine bearing cooling inlet plate
US9291089B2 (en) 2012-08-31 2016-03-22 Caterpillar Inc. Turbocharger having compressor cooling arrangement and method
JP2014111905A (ja) 2012-12-05 2014-06-19 Mitsubishi Heavy Ind Ltd 遠心圧縮機およびこれを備えた過給機ならびに遠心圧縮機の運転方法
JP6015843B2 (ja) * 2013-02-21 2016-10-26 トヨタ自動車株式会社 ブローバイガス環流装置を備えた内燃機関の過給機の冷却装置
CN104653479B (zh) 2013-11-22 2017-05-10 珠海格力电器股份有限公司 离心式压缩机及具有其的冷水机组
US11377954B2 (en) * 2013-12-16 2022-07-05 Garrett Transportation I Inc. Compressor or turbine with back-disk seal and vent
US9732766B2 (en) * 2014-02-19 2017-08-15 Honeywell International Inc. Electric motor-driven compressor having a heat shield forming a wall of a diffuser
DE102014012764A1 (de) * 2014-09-02 2016-03-03 Man Diesel & Turbo Se Radialverdichterstufe
JP6225092B2 (ja) * 2014-10-17 2017-11-01 三菱重工業株式会社 ラビリンスシール、遠心圧縮機及び過給機
US10968917B2 (en) * 2014-10-27 2021-04-06 Zhongshan Broad-Ocean Motor Manufacturing Co., Ltd. Blower comprising a pressure measuring connector
US10830144B2 (en) 2016-09-08 2020-11-10 Rolls-Royce North American Technologies Inc. Gas turbine engine compressor impeller cooling air sinks
WO2019073584A1 (fr) * 2017-10-12 2019-04-18 三菱重工エンジン＆ターボチャージャ株式会社 Boîtier de compresseur et turbocompresseur comportant ledit boîtier de compresseur
US11525393B2 (en) 2020-03-19 2022-12-13 Rolls-Royce Corporation Turbine engine with centrifugal compressor having impeller backplate offtake
US11773773B1 (en) 2022-07-26 2023-10-03 Rolls-Royce North American Technologies Inc. Gas turbine engine centrifugal compressor with impeller load and cooling control
CN115324911B (zh) * 2022-10-12 2023-08-22 中国核动力研究设计院 超临界二氧化碳压气机以及同轴发电系统
CN115450950B (zh) * 2022-11-08 2023-03-03 中国核动力研究设计院 压气机和超临界二氧化碳发电系统

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Publication number Priority date Publication date Assignee Title
US11199201B2 (en) 2016-02-22 2021-12-14 Mitsubishi Heavy Industries Marine Machinery & Equipment Co., Ltd. Impeller back surface cooling structure and supercharger

Also Published As

Publication number Publication date
DE59809488D1 (de) 2003-10-09
CN1102706C (zh) 2003-03-05
CN2381815Y (zh) 2000-06-07
JP2000054997A (ja) 2000-02-22
CZ177899A3 (cs) 2000-07-12
KR100537036B1 (ko) 2005-12-16
TW562900B (en) 2003-11-21
CZ291692B6 (cs) 2003-05-14
US6238179B1 (en) 2001-05-29
KR19990088489A (ko) 1999-12-27
JP4503726B2 (ja) 2010-07-14
EP0961034A1 (fr) 1999-12-01
CN1239193A (zh) 1999-12-22

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