EP0749533B1 - Compresseur - Google Patents

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Publication number
EP0749533B1
EP0749533B1 EP95907077A EP95907077A EP0749533B1 EP 0749533 B1 EP0749533 B1 EP 0749533B1 EP 95907077 A EP95907077 A EP 95907077A EP 95907077 A EP95907077 A EP 95907077A EP 0749533 B1 EP0749533 B1 EP 0749533B1
Authority
EP
European Patent Office
Prior art keywords
shaft
compressor
impeller
rotor
bearing
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
EP95907077A
Other languages
German (de)
English (en)
Other versions
EP0749533A1 (fr
Inventor
Richard Gozdawa
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.)
Welsh Innovations Ltd
Original Assignee
Welsh Innovations Ltd
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 Ltd filed Critical Welsh Innovations Ltd
Publication of EP0749533A1 publication Critical patent/EP0749533A1/fr
Application granted granted Critical
Publication of EP0749533B1 publication Critical patent/EP0749533B1/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
    • 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
    • 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
    • F04D29/05—Shafts or bearings, or assemblies thereof, specially adapted for elastic fluid pumps
    • F04D29/051—Axial thrust balancing
    • F04D29/0513—Axial thrust balancing hydrostatic; hydrodynamic thrust bearings
    • 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
    • F04D29/06—Lubrication
    • F04D29/063—Lubrication specially adapted for elastic fluid pumps

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 0.27kg per second is within one of the market bands for a dry air compressor. Delivery pressures can be met without difficulty 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.
  • EP-A-0 150599 discloses a compressor comprising a rotatable shaft, bearing means provided for the shaft, drive means arranged to rotate the shaft, at least two impeller rotor stages mounted in spaced relationship on the shaft, at least a portion of the rotatable shaft between the spaced rotor stages being substantially hollow.
  • compressed air or working gas is bled from a relatively higher pressure rotor stage toward relatively lower pressure rotor stage along a path comprising the hollow portion of the rotatable shaft.
  • bleed passage means communicating with the hollow portion of the shaft is provided for this purpose. This is advantageous because the shaft is effectively cooled which results in further heat dissipation from the bearings.
  • the hollow portion of the shaft reduces the rotational moment of inertia of the combined impeller rotor stage and shaft assembly, thereby reducing the work needed to rotate the shaft and hence improving efficiency.
  • thrust bearing means is provided, arranged to act directly on the impeller rotor stage such that when the shaft rotates, bearing contact is made between the thrust bearing and a bearing surface of the impeller rotor stage.
  • the compressor is provided with direct drive means arranged to rotate the shaft at high rotational speeds preferably in the range 50,000 to 100,000rpm.
  • the drive means therefore comprises an electric motor having a rotor mounted on the shaft.
  • the electric motor is positioned between the rotor stages. It is preferred that thrust bearing means is arranged to act directly on at least two impeller rotor stages to take up axial forces in opposed axial directions of the shaft.
  • intercooler means is provided intermediate impeller rotor stages to enhance the efficiency of the compressor.
  • the shaft comprises a composite shaft comprising the hollow rotor portion intermediately connecting spaced portions of the shaft, the spaced portions of the shaft desirably carrying respective impeller stages.
  • the hollow rotor portion of the shaft is of a magnetic or magnetisable material.
  • securing means for securing the hollow rotor portion and spaced portions of the shaft relative to one another.
  • the securing means comprises a tie rod passing through the hollow rotor portion and the connected spaced portions of the shaft.
  • thrust bearing means are provided to act on impeller stages at both spaced portions of the shaft arranged such that axial thrust of the shaft in mutually opposed axial directions is taken up.
  • the thrust bearing means is arranged to act on the respective impeller stage rotor such that heat generated at the bearing is transferred to the impeller stage rotor.
  • the thrust bearing means and the respective impeller are therefore preferably arranged to be in thermally communicative bearing contact when the compressor is operational.
  • the compressor further comprises journal bearing means arranged to support the shaft, preferably comprising at least one tilting pad journal bearing advantageously arranged to be self generating and air or gas lubricated and desirably 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 journal bearing means is arranged to act.
  • the bearing means comprises at least two journal bearings, each preferably being tilting pad journal bearings arranged to be air or gas lubricated and having bearing pads provided with respective ceramics bearing surfaces.
  • foil journal bearings may be used.
  • 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 thrust bearing means preferably comprises a thrust bearing having tilting pads acting against the impeller rotor stage.
  • the thrust bearing is of a self-generating air-or gas-lubricated type, having pads provided with ceramics bearing surfaces.
  • 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.
  • At least two of the 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.
  • FIG. 1 there is shown a compressor generally designated 1 which is generally as described in PCT specification WO94/05913. Although similar in general construction, and illustrative of preferred features, the compressor shown in Figures 1 and 2 does not include the specific structural features which result in the improved performance of a compressor according to the invention.
  • 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 cpposed 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.
  • the bearing surface portions of the shaft are coated with hardened deposit to increase wear resistance.
  • Thrust bearing 10 is also provided with tilting pad thrust members 10a,10b provided with ceramics bearing surfaces.
  • Pads 10a are arranged to take up normal thrust loading transferred from shaft 2 by thrust collar 11 during normal running of the compressor.
  • Pads 10b act on the opposite side of collar 11 and act to take up reverse thrust loading during motor and shaft "run up" to normal operational speed.
  • an intercooler 15 is provided intermediately between first stage impeller 4 and second stage impeller 5.
  • a second intercooler 16 is provided intermediately between second stage impeller 5 and final (third) stage impeller 6. It is an important feature of the compressor that the flow of working gas into the first stage impeller 4 is in an opposed direction to the flow of working gas into the second and third stage impellers 5,6. This has the effect of "balancing" the axial thrust acting on the shaft and reducing the usual axial thrust applied to thrust bearing 10. Bearing losses in thrust bearing 10 are thereby minimised.
  • intercooler 15 In operation, the electric motor is run up to an operating speed of around 80,000 r.p.m. Working gas is then drawn axially into the first impeller stage 4 and forced out through duct 17 into intercooler 15. The working gas leaves intercooler 15 entering duct 18 and subsequently passing axially into second impeller stage 5. The working fluid leaves impeller 5 radially passing via duct 19 into second intercooler 16. Intercoolers 15 and 16 are substantially identical, except that intercooler 16 is arranged with its longitudinal dimension 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 third (and final) impeller stage 6 axially.
  • the working gas leaves the final impeller stage 6 radially via outlet duct 21 (the outlet flow through duct 21 is out of the page in Figure 1).
  • the compressor Due to the combination of the high speed directly driven rotatable shaft, together with the minimisation of bearing losses and the split stage intercooled arrangement of the impeller rotors, an extremely efficient compressor is provided.
  • the compressor enables a compact turbomachine to be used in applications previously served mainly by screw feed type compressors since, unusually for a turbo compressor high delivery pressures (8.5 bara typically) are achievable with relatively low mass flows (0.27 kg/s typically for air).
  • compressor 101 shown is generally similar to in terms of construction and operation to the arrangement shown in Figures 1 and 2, and like reference numerals have been used to identify like components of the compressors.
  • the thrust collar 11 of the compressor embodiment shown in Figure 2 is dispensed with and a pair of spaced thrust bearings 210a,210b provided adjacent the first and second stage impellers 4,5 respectively to take up axial forces in respectively opposed directions acting on the shaft 2. It has been found that with the compressor shown in Figure 1, excessive heat is generated at the thrust bearing 10 which results in reduced efficiency in terms of compressor performance and operational life expectancy. By replacing the thrust collar 11 and bearing assembly 10 with thrust bearings 210a,210b acting directly on the rear substantially flat surfaces of impeller rotor stages 4,5 respectively (as shown in the embodiment of Figure 3), overheating problems are substantially ameliorated.
  • the thrust bearings 210a,210b comprise bearing pads 110a,110b mounted in a respective annular support ring 37a,37b carried by housings 35a,35b.
  • the pads may be homogenous ceramics material, or alternatively may be provided with a ceramics bearing surface.
  • the embodiment of the invention shown in Figure 3 also differs from the arrangement shown in Figure 1 in that the shaft effectively comprises a hollow sectioned composite shaft comprising a first shaft portion 2a carrying impeller stage rotor 4), a second shaft portion 2b (carrying impeller stage rotor 5), and intermediate motor rotor section 7 extending between shaft portions 2a and 2b.
  • Shaft portions 2a and 2b connect with opposed ends of the motor rotor section 7, the whole composite shaft being held together by means of axially extending tie rod 25.
  • First and second shaft portions 2a, 2b are provided with respective hollow cylindrical cavities 31, 32 intersected by the axis of the shaft.
  • Tie rod 25 is provided along its length with sets of circumferentially spaced projections 40 which abut internal axial bores of shaft portions 2a, 2b and motor rotor 7. Circumferential spaces intermediate respective projections in each set 40 permit air communication along substantially the entire length of the interior of the composite shaft in the region adjacent tie rod 25. Compressed air or working gas is bled back from relatively higher pressure stage 5 (via bleed communication passage 42) and passes internally along the length of the composite shaft toward relatively lower pressure stage 4. Passage of the air or transport gas in the internal cavities 31, 32 and along the tie rod cause heat dissipation from the shaft portions 2a, 2b (and hence bearings 210a, 210b, 108, 109) and motor rotor 7.
  • journal bearings 108, 109 are provided at opposed ends of the shaft and have bearings 112 which act on respective shaft portions 2a, 2b. Aided by the presence of cavities 31, 32 heat generated in the shaft from bearing contact with the journal bearings is transferred directly to impeller 5, 4 where it is transferred to the working gas of the compressor.
  • the respective thrust bearing 210a, 210b and journal bearing 108, 109 are provided in a respective common unitary housing 35a, 35b.
  • the compressor shown in Figures 3 and 4 operates in an almost identical manner to the compressor shown in Figure 1.
  • Intercoolers (not shown) are provided intermediate each impeller rotor stage 4,5,6 and flow of working gas through the compressor is substantially as described in relation to the compressor shown in Figure 1.

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

Claims (10)

  1. Compresseur (101) comprenant un arbre rotatif (2), des moyens de palier (8,9) prévus pour l'arbre, un moyen de commande (7, 23) disposé pour faire tourner l'arbre, au moins deux étages de roues de rotor (4, 5, 6) montés de façon espacée sur l'arbre, au moins une portion (31, 32) de l'arbre rotatif entre les étages de rotor espacés (4, 5, 6) étant essentiellement creuse, caractérisé en ce que de l'air comprimé ou du gaz actif est purgé àepuis un étage de rotor (5) à pression relativement élevée vers un étage de rotor (4) à pression relativement basse le long d'un trajet comprenant la portion creuse (31, 32) de l'arbre rotatif.
  2. Compresseur (101) selon la revendication 1, caractérisé en ce que l'arbre comprend un arbre composite comprenant une portion de rotor (7) connectant de façon intermédiaire des portions espacées (2a, 2b) de l'arbre 123), les portions espacées étant munies de cavités axiales respectives (31, 32) et portant des étages de roues de rotor respectifs (4, 5).
  3. Compresseur (101) selon la revendication 1 ou la revendication 2, caractérisé en ce que la portion creuse (31, 32) de l'arbre est en un matériau magnétique ou susceptible d'être magnétisé.
  4. Compresseur (101) selon l'une quelconque des revendications précédentes, caractérisé en ce que le moyen de commande (7, 23) comprend des moyens de commande électromagnétiques, comprenant de préférence un moteur électrique ayant un rotor (7) monté sur l'arbre (2).
  5. Compresseur (101) selon l'une quelconque des revendications précédentes, caractérisé en ce que des moyens de palier de butée (210a, 210b) sont arrangés pour agir directement sur les étages de roues de rotor (4, 5) pour reprendre les forces agissant dans la direction axiale de l'arbre.
  6. Compresseur (101) selon l'une quelconque des revendications précédentes, caractérisé en ce qu'un moyen de refroidisseur intermédiaire (15, 16) est prévu entre les étages de roues de rotor (4, 5).
  7. Compresseur (101) selon l'une quelconque des revendications précédentes, caractérisé en ce que le compresseur comprend en outre un moyen de palier intermédiaire (108, 109) disposé pour supporter l'arbre.
  8. Compresseur (101) selon la revendication 7, caractérisé en ce que le moyen de palier intermédiaire (108, 109) comprend au moins un palier intermédiaire à patins oscillants.
  9. Compresseur (101) selon l'une quelconque des revendications précédentes, caractérisé en ce que les étages de roues de rotor (4, 5, 6) font saillie aux extrémités opposées de l'arbre (2).
  10. Compresseur (101) selon l'une quelconque des revendications précédentes, caractérisé en ce que les étages de roue de rotor sont disposés selon une configuration inversée (4, 6 et 4, 5) l'un par rapport à l'autre, de sorte que les flux respectifs à l'intérieur des étages de roues respectifs sont dans des directions opposées.
EP95907077A 1994-03-08 1995-01-31 Compresseur Expired - Lifetime EP0749533B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
GB9404436A GB9404436D0 (en) 1994-03-08 1994-03-08 Compressor
GB9404436 1994-03-08
PCT/GB1995/000193 WO1995024563A1 (fr) 1994-03-08 1995-01-31 Compresseur

Publications (2)

Publication Number Publication Date
EP0749533A1 EP0749533A1 (fr) 1996-12-27
EP0749533B1 true EP0749533B1 (fr) 1998-09-23

Family

ID=10751462

Family Applications (1)

Application Number Title Priority Date Filing Date
EP95907077A Expired - Lifetime EP0749533B1 (fr) 1994-03-08 1995-01-31 Compresseur

Country Status (7)

Country Link
EP (1) EP0749533B1 (fr)
JP (1) JPH09509999A (fr)
AT (1) ATE171520T1 (fr)
AU (1) AU1541495A (fr)
DE (1) DE69504961T2 (fr)
GB (1) GB9404436D0 (fr)
WO (1) WO1995024563A1 (fr)

Families Citing this family (23)

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Publication number Priority date Publication date Assignee Title
GB9602126D0 (en) * 1996-02-02 1996-04-03 Compact Radial Compressors Ltd Compressors
GB9716494D0 (en) 1997-08-05 1997-10-08 Gozdawa Richard J Compressions
EP1074746B1 (fr) * 1999-07-16 2005-05-18 Man Turbo Ag Turbo-compresseur
EP0990798A1 (fr) * 1999-07-16 2000-04-05 Sulzer Turbo AG Turbo-compresseur
EP1069313B1 (fr) 1999-07-16 2005-09-14 Man Turbo Ag Turbo-compresseur
DE10056773B4 (de) * 2000-11-16 2006-01-12 AEG Hausgeräte GmbH Radiallüfter
GB2384274A (en) * 2002-01-16 2003-07-23 Corac Group Plc Downhole compressor with electric motor and gas bearings
DE10214307A1 (de) * 2002-03-28 2003-10-23 Nash Elmo Ind Gmbh Verdichtereinheit
ITMI20060294A1 (it) 2006-02-17 2007-08-18 Nuovo Pignone Spa Motocompressore
FR2922970A1 (fr) * 2007-10-25 2009-05-01 Airtechnologies Appareil de compression de gaz
US8062400B2 (en) 2008-06-25 2011-11-22 Dresser-Rand Company Dual body drum for rotary separators
DE102008057472B4 (de) * 2008-11-14 2011-07-14 Atlas Copco Energas GmbH, 50999 Mehrstufiger Radial-Turboverdichter
IT1399171B1 (it) 2009-07-10 2013-04-11 Nuovo Pignone Spa Unita' di compressione ad alta pressione per fluidi di processo di impianti industriali e relativo metodo di funzionamento
JP4856748B2 (ja) * 2009-10-22 2012-01-18 本田技研工業株式会社 過給機
EP2533905B1 (fr) 2010-02-10 2018-07-04 Dresser-Rand Company Collecteur de fluide séparateur et procédé
JP5094897B2 (ja) * 2010-03-08 2012-12-12 本田技研工業株式会社 電動遠心圧縮機
US8994237B2 (en) 2010-12-30 2015-03-31 Dresser-Rand Company Method for on-line detection of liquid and potential for the occurrence of resistance to ground faults in active magnetic bearing systems
WO2013109235A2 (fr) 2010-12-30 2013-07-25 Dresser-Rand Company Procédé de détection en ligne de défauts de résistance à la masse dans des systèmes de palier magnétique actif
WO2012138545A2 (fr) 2011-04-08 2012-10-11 Dresser-Rand Company Système de refroidissement à circulation d'huile diélectrique pour paliers enfermés et dispositifs électroniques enfermés
EP2715167B1 (fr) 2011-05-27 2017-08-30 Dresser-Rand Company Roulement segmenté à décélération en roue libre pour des systèmes de roulement magnétique
US8851756B2 (en) 2011-06-29 2014-10-07 Dresser-Rand Company Whirl inhibiting coast-down bearing for magnetic bearing systems
CZ304896B6 (cs) * 2013-02-01 2015-01-07 Radovan Kundera Zařízení pro chlazení rotoru turbostroje
US10669850B2 (en) * 2016-12-22 2020-06-02 Brian Blackwell Impeller-type liquid ring compressor

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CH663644A5 (de) * 1982-02-22 1987-12-31 Bbc Brown Boveri & Cie Turboverdichter.
IL73770A (en) * 1983-12-16 1990-06-10 Garrett Corp Air cycle cooling machine and an arrangement for cooling an aircraft cabin comprising the same
DE3600124A1 (de) * 1986-01-04 1987-07-16 Fortuna Werke Maschf Ag Geblaese zum umwaelzen grosser gasmengen, insbesondere fuer hochleistungs-laser
EP0297691A1 (fr) * 1987-06-11 1989-01-04 Acec Energie S.A. Ensemble moteur-compresseur
JPH05502076A (ja) * 1989-12-20 1993-04-15 アライド・シグナル・インコーポレーテツド 可変速ターボ真空ポンプ
GB9219167D0 (en) * 1992-09-10 1992-10-28 Derivative Technology Limited Compressor

Also Published As

Publication number Publication date
JPH09509999A (ja) 1997-10-07
DE69504961T2 (de) 1999-07-01
EP0749533A1 (fr) 1996-12-27
AU1541495A (en) 1995-09-25
DE69504961D1 (de) 1998-10-29
GB9404436D0 (en) 1994-04-20
WO1995024563A1 (fr) 1995-09-14
ATE171520T1 (de) 1998-10-15

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