WO1994005913A1 - Compresseur - Google Patents

Compresseur Download PDF

Info

Publication number
WO1994005913A1
WO1994005913A1 PCT/GB1993/001900 GB9301900W WO9405913A1 WO 1994005913 A1 WO1994005913 A1 WO 1994005913A1 GB 9301900 W GB9301900 W GB 9301900W WO 9405913 A1 WO9405913 A1 WO 9405913A1
Authority
WO
WIPO (PCT)
Prior art keywords
shaft
bearing
compressor according
impeller
stages
Prior art date
Application number
PCT/GB1993/001900
Other languages
English (en)
Inventor
Richard Gozdawa
Original Assignee
Welsh Innovations Limited
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 Welsh Innovations Limited filed Critical Welsh Innovations Limited
Priority to DE69317791T priority Critical patent/DE69317791T2/de
Priority to EP94908821A priority patent/EP0667934B1/fr
Priority to JP6507023A priority patent/JPH08501367A/ja
Priority to AU49767/93A priority patent/AU682318B2/en
Publication of WO1994005913A1 publication Critical patent/WO1994005913A1/fr

Links

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
    • F04D29/05—Shafts or bearings, or assemblies thereof, specially adapted for elastic fluid pumps
    • F04D29/056—Bearings
    • F04D29/057—Bearings hydrostatic; hydrodynamic
    • 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
    • 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
    • F04D25/02—Units comprising pumps and their driving means
    • F04D25/06—Units comprising pumps and their driving means the pump being electrically driven
    • F04D25/0606—Units comprising pumps and their driving means the pump being electrically driven the electric motor being specially adapted for integration in the pump
    • 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
    • F04D29/5826—Cooling at least part of the working fluid in a heat exchanger

Definitions

  • the present invention relates to a compressor.
  • the overall market for air compressors comprises a number of performance bands with each performance band encompassing in combination a range of delivery pressures and a range of mass flows.
  • a delivery pressure of around 8.5 bara combined with a mass flow of 0.27 kg per second is within one of the market bands for a dry air compressor. Delivery pressures can be met without difficult at the present time, but the mass flow from a conventional turbo compressor of this sort is far greater than the mass flow which is required.
  • turbo compressors mounted on known oil lubricated, roller or ball journal bearings would be prohibitively inefficient at the high shaft rotational speeds (typically 50,000 to 100,000 rpm) required for the desired performance.
  • Known turbo compressors operating in this band would therefore be extremely expensive, large and inefficient.
  • a compressor comprising:
  • drive means arranged to rotate the shaft, the drive means comprising an electric motor having a rotor mounted on the shaft;
  • bearing means provided for the shaft, the bearing means comprising at least one tilting pad journal bearing arranged to be self generating and air or gas lubricated, and having bearing pads provided with a ceramics bearing surface.
  • the bearing pads may comprise homogenous pads of ceramics material.
  • the shaft is provided with hardened or ceramics surface portions against which the ceramics bearing surface of the respective tilting pads of the bearing means is arranged to act.
  • the bearing means comprises at least two journal bearings, each being tilting pad journal bearings arranged to be air or gas lubricated and having bearing pads provided with respective ceramics bearing surfaces.
  • the journal bearings are provided to support spaced portions of the shaft advantageously adjacent opposed ends of the electric motor. It is preferred that at least one journal bearing is provided intermediately between a respective end of the motor and a respective impeller rotor stage.
  • the shaft is supported by at least one thrust bearing which is also preferably a self generating air or gas lubricated bearing.
  • a thrust bearing preferably comprises tilting pads acting against hardened, or ceramics surfaced portions of the shaft (or a thrust collar provided thereon). It is preferred that the thrust bearing is arranged to counteract axial shaft thrust acting in mutually opposed axial directions.
  • each impeller rotor stage comprises a respective compressor impeller, with intercooler means being communicatively connected intermediate the impeller rotor stages.
  • each impeller rotor is provided such that the compressor comprises three compression stages. It is preferred that respective intercooler means is provided intermediately between successive compressor stages. This improves the efficiency of the compressor.
  • the flow of working gas into each respective impeller rotor is axial, and preferably in the direction of the electric motor.
  • impeller stages are arranged in reverse formation relative to one another such that the respective flows into the respective impeller stages are in opposed directions, preferably towards one another.
  • seal means preferably comprising respective labyrinth seals, are provided for the shaft, arranged to inhibit access of the working gas from the impeller rotor stages to the motor and bearing means.
  • the electric motor comprises an electromagnetic or permanent magnet electric motor, preferably arranged to rotate the shaft at over 50,000 r.p.m. and more preferably at over 70,000 r.p.m.
  • the electric motor is a direct current motor, preferably controlled by a variable frequency source.
  • Figure 1 is a schematic representation of a compressor according to the invention.
  • Figure 2 is an enlarged detail of a part of the compressor of Figure 1.
  • the compressor 1 comprises an axial rotatable shaft 2 mounted in a housing 3, and having machined aluminium impeller rotors 4,5,6 mounted thereon.
  • first stage, rotor 4 is overhung at one end of the shaft, whereas second and third stage rotors 5 and 6 respectively are overhung at the opposed end.
  • a brushless D.C. motor having a rotor 7 comprising permanent magnets mounted on the shaft 2 and a stator 23 mounted in the housing.
  • a solid state thyristor based inverter/controller (not shown) is used to generate a variable but high frequency current from a standard 415V/50Hz electrical supply. The high frequency current drives the motor (and therefore directly drives the shaft 2 without the need for intermediate gearing) at the required high operational speed which is typically of the order of 50,000 to 100,000 r.p.m. Because no gearing is required to couple shaft 2 to the drive, power losses are minimised.
  • the shaft 2 is supported in housing 3 on journal bearings 8,9 provided at either end of the electric motor, adjacent impeller rotors 4 and 5 respectively.
  • a thrust bearing 10 is also mounted in the housing to act on thrust collar 11 provided on the shaft.
  • Journal bearing 8,9 comprise tilting pad journal bearings which are self generating and air lubricated.
  • the tilting pads 12 of each journal bearing 8,9 are supported on flexible pivots 24, and provided with ceramics bearing surfaces 13 which are arranged to act on immediately adjacent bearing surface portions of the shaft.
  • Thrust bearing 10 is also provided with tilting pad thrust members 10a, 1 provided with ceramics bearing surfaces.
  • Pads 10a are arranged to take up normal thr loading transferred from shaft 2 by thrust collar 11 during normal running of the compress
  • Pads 10b act on the opposite side of collar 11 and act to take up reverse thrust loading du motor and shaft "run up" to normal operational speed.
  • an intercooler 15 is provided intermediately betw first stage impeller 4 and second stage impeller 5.
  • a second intercooler 16 is provi intermediately between second stage impeller 5 and final (third) stage impeller 6. It is important feature of the compressor that the flow of working gas into the first stage impel 4 is in an opposed direction to the flow of working gas into the second and third st impellers 5,6. This has the effect of "balancing" the axial thrust acting on the shaft reducing the usual axial thrust applied to thrust bearing 10. Bearing losses in thrust beari 10 are thereby minimised.
  • the electric motor is run up to an operating speed of arou 80,000 r.p.m.
  • Working gas is then drawn axially into the first impeller stage 4 and forc out through duct 17 into intercooler 15.
  • the working gas leaves intercooler 15 entering d 18 and subsequently passing axially into second impeller stage 5.
  • the working fluid leav impeller 5 radially passing via duct 19 into second intercooler 16.
  • Intercoolers 15 and 6 substantially identical, except that intercooler 16 is arranged with its longitudinal dimens at 90° to the longitudinal dimension of intercooler 15 (i.e. the longitudinal dimension of intercooler 16 is out of the page in Figure 1).
  • Working gas leaves intercooler 16 via duct 20 and is directed to enter the th (and final) impeller stage 6 axially.
  • the working gas leaves the final impeller stag radially via outlet duct 21 (the outlet flow through duct 21 is out of the page in Figure
  • an extremely efficient compressor is provided according to invention.
  • the compressor enables a compact turbomachine to be used in applicati previously served mainly be screw feed type compressors since, unusually for a tur compressor high delivery pressures (8.5 bara typically) are achievable with relatively l mass flows (0.27 kg/s typically for air).

Abstract

Un compresseur (1) comprend un arbre rotatif (2) entraîné par un moteur électrique (7, 23) ayant un rotor (7) monté sur l'arbre (2). L'arbre (2) porte au moins deux étages de rotors à ailettes (4, 5, 6) agencés de manière à ce que le moteur se trouve entre les étages de rotors à ailettes. Un refroidisseur intermédiaire (15) est connecté entre les étages des rotors à ailettes (4, 5, 6) et l'arbre (2) est supporté par des moyens de paliers (8, 9, 10) comprenant au moins un palier de tourillon à patins inclinables agencé pour être autogénérateur, lubrifié par de l'air ou par un gaz, et pourvu de patins de palier avec une surface d'appui en céramique. Le compresseur (1) est extrêmement efficace et il est particulièrement utile dans une utilisation avec de l'air sec où il est important d'éviter la contamination du gaz de travail en utilisant des paliers qui ne sont pas lubrifiés avec une huile.
PCT/GB1993/001900 1992-09-10 1993-09-08 Compresseur WO1994005913A1 (fr)

Priority Applications (4)

Application Number Priority Date Filing Date Title
DE69317791T DE69317791T2 (de) 1992-09-10 1993-09-08 Verdichter
EP94908821A EP0667934B1 (fr) 1992-09-10 1993-09-08 Compresseur
JP6507023A JPH08501367A (ja) 1992-09-10 1993-09-08 圧縮機
AU49767/93A AU682318B2 (en) 1992-09-10 1993-09-08 Compressor

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
GB929219167A GB9219167D0 (en) 1992-09-10 1992-09-10 Compressor
GB9219167.5 1992-09-10

Publications (1)

Publication Number Publication Date
WO1994005913A1 true WO1994005913A1 (fr) 1994-03-17

Family

ID=10721708

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/GB1993/001900 WO1994005913A1 (fr) 1992-09-10 1993-09-08 Compresseur

Country Status (13)

Country Link
EP (1) EP0667934B1 (fr)
JP (1) JPH08501367A (fr)
CN (1) CN1086587A (fr)
AT (1) ATE164662T1 (fr)
AU (1) AU682318B2 (fr)
CA (1) CA2144181A1 (fr)
DE (1) DE69317791T2 (fr)
GB (1) GB9219167D0 (fr)
IL (1) IL106924A (fr)
MY (1) MY109678A (fr)
RU (1) RU2118714C1 (fr)
WO (1) WO1994005913A1 (fr)
ZA (1) ZA936403B (fr)

Cited By (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO1995024563A1 (fr) * 1994-03-08 1995-09-14 Welsh Innovations Limited Compresseur
US5795138A (en) * 1992-09-10 1998-08-18 Gozdawa; Richard Compressor
WO1999031390A1 (fr) * 1997-12-03 1999-06-24 Sundyne Corporation Procede de production de gaz en surpression
EP1321680A2 (fr) 2001-12-22 2003-06-25 Miscel Oy Turbomachine
DE10163950A1 (de) * 2001-12-22 2003-07-03 Miscel Oy Ltd Gas-Kompressor
GB2384274A (en) * 2002-01-16 2003-07-23 Corac Group Plc Downhole compressor with electric motor and gas bearings
WO2003072946A1 (fr) * 2002-02-28 2003-09-04 Turbocor Inc. Compresseur centrifuge
US6710487B2 (en) 2000-01-11 2004-03-23 Gsi Lumonics Corporation Rotary device with matched expansion ceramic bearings
WO2015157434A1 (fr) * 2014-04-08 2015-10-15 Caire Inc. Systèmes rotatifs lubrifiés par un fluide en cours de traitement
AU2015402113B2 (en) * 2015-07-16 2019-09-12 Kingclean Electric Co., Ltd. High-speed hall-less three-phase vacuum cleaner motor

Families Citing this family (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH11294879A (ja) * 1998-02-16 1999-10-29 Daikin Ind Ltd 冷凍装置
RU2150609C1 (ru) * 1999-02-18 2000-06-10 Научно-исследовательский институт низких температур при МАИ Центробежный компрессорный агрегат и электродвигатель
EP1353041A1 (fr) * 2002-04-12 2003-10-15 ABB Turbo Systems AG Turbocompresseur avec moyens sur l'arbre pour le confinement axial dudit arbre en cas d'éclatement de la roue de compresseur
CN102151852B (zh) * 2011-04-27 2012-06-27 天津大学 一种动静压陶瓷主轴装置
RU2533948C2 (ru) * 2013-03-12 2014-11-27 Федеральное Государственное Автономное Образовательное Учреждение Высшего Профессионального Образования "Дальневосточный Федеральный Университет" (Двфу) Упорный подшипниковый узел
RU2529070C1 (ru) * 2013-03-12 2014-09-27 Федеральное Государственное Автономное Образовательное Учреждение Высшего Профессионального Образования "Дальневосточный Федеральный Университет" (Двфу) Упорный подшипниковый узел
RU2542806C1 (ru) * 2013-08-08 2015-02-27 Федеральное Государственное Автономное Образовательное Учреждение Высшего Профессионального Образования "Дальневосточный Федеральный Университет" (Двфу) Упорный подшипниковый узел

Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3933416A (en) * 1945-05-01 1976-01-20 Donelian Khatchik O Hermatically sealed motor blower unit with stator inside hollow armature
DE2541715A1 (de) * 1974-09-20 1976-04-01 Hitachi Ltd Turbo-aggregat
GB1512381A (en) * 1975-05-06 1978-06-01 Nat Res Dev Gas compression apparatus including an axial thrust bearing
EP0087197A1 (fr) * 1982-02-22 1983-08-31 BBC Aktiengesellschaft Brown, Boveri & Cie. Entraînement et système de paliers pour un turbo-compresseur
FR2528127A1 (fr) * 1982-06-04 1983-12-09 Creusot Loire Moto-compresseur centrifuge electrique integre a grande vitesse
EP0297691A1 (fr) * 1987-06-11 1989-01-04 Acec Energie S.A. Ensemble moteur-compresseur
EP0305700A2 (fr) * 1987-09-03 1989-03-08 MAN Gutehoffnungshütte Aktiengesellschaft Ensemble de compresseur
JPH03121306A (ja) * 1989-10-02 1991-05-23 Toshiba Corp ティルティングパッド形動圧気体軸受

Patent Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3933416A (en) * 1945-05-01 1976-01-20 Donelian Khatchik O Hermatically sealed motor blower unit with stator inside hollow armature
DE2541715A1 (de) * 1974-09-20 1976-04-01 Hitachi Ltd Turbo-aggregat
GB1512381A (en) * 1975-05-06 1978-06-01 Nat Res Dev Gas compression apparatus including an axial thrust bearing
EP0087197A1 (fr) * 1982-02-22 1983-08-31 BBC Aktiengesellschaft Brown, Boveri & Cie. Entraînement et système de paliers pour un turbo-compresseur
FR2528127A1 (fr) * 1982-06-04 1983-12-09 Creusot Loire Moto-compresseur centrifuge electrique integre a grande vitesse
EP0297691A1 (fr) * 1987-06-11 1989-01-04 Acec Energie S.A. Ensemble moteur-compresseur
EP0305700A2 (fr) * 1987-09-03 1989-03-08 MAN Gutehoffnungshütte Aktiengesellschaft Ensemble de compresseur
JPH03121306A (ja) * 1989-10-02 1991-05-23 Toshiba Corp ティルティングパッド形動圧気体軸受

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
PATENT ABSTRACTS OF JAPAN vol. 015, no. 321 (M - 1147) 15 August 1991 (1991-08-15) *

Cited By (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5795138A (en) * 1992-09-10 1998-08-18 Gozdawa; Richard Compressor
WO1995024563A1 (fr) * 1994-03-08 1995-09-14 Welsh Innovations Limited Compresseur
WO1999031390A1 (fr) * 1997-12-03 1999-06-24 Sundyne Corporation Procede de production de gaz en surpression
US6710487B2 (en) 2000-01-11 2004-03-23 Gsi Lumonics Corporation Rotary device with matched expansion ceramic bearings
EP1321680A2 (fr) 2001-12-22 2003-06-25 Miscel Oy Turbomachine
DE10163950A1 (de) * 2001-12-22 2003-07-03 Miscel Oy Ltd Gas-Kompressor
GB2384274A (en) * 2002-01-16 2003-07-23 Corac Group Plc Downhole compressor with electric motor and gas bearings
WO2003072946A1 (fr) * 2002-02-28 2003-09-04 Turbocor Inc. Compresseur centrifuge
US7240515B2 (en) 2002-02-28 2007-07-10 Turbocor, Inc. Centrifugal compressor
WO2015157434A1 (fr) * 2014-04-08 2015-10-15 Caire Inc. Systèmes rotatifs lubrifiés par un fluide en cours de traitement
AU2015402113B2 (en) * 2015-07-16 2019-09-12 Kingclean Electric Co., Ltd. High-speed hall-less three-phase vacuum cleaner motor

Also Published As

Publication number Publication date
JPH08501367A (ja) 1996-02-13
IL106924A (en) 1996-10-16
CN1086587A (zh) 1994-05-11
EP0667934B1 (fr) 1998-04-01
RU95109152A (ru) 1997-02-20
ZA936403B (en) 1994-08-08
MY109678A (en) 1997-04-30
EP0667934A1 (fr) 1995-08-23
GB9219167D0 (en) 1992-10-28
ATE164662T1 (de) 1998-04-15
DE69317791D1 (de) 1998-05-07
AU4976793A (en) 1994-03-29
IL106924A0 (en) 1993-12-28
RU2118714C1 (ru) 1998-09-10
CA2144181A1 (fr) 1994-03-17
DE69317791T2 (de) 1998-12-10
AU682318B2 (en) 1997-10-02

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