EP0667934B1 - Verdichter - Google Patents
Verdichter Download PDFInfo
- Publication number
- EP0667934B1 EP0667934B1 EP94908821A EP94908821A EP0667934B1 EP 0667934 B1 EP0667934 B1 EP 0667934B1 EP 94908821 A EP94908821 A EP 94908821A EP 94908821 A EP94908821 A EP 94908821A EP 0667934 B1 EP0667934 B1 EP 0667934B1
- Authority
- EP
- European Patent Office
- Prior art keywords
- shaft
- bearing
- compressor according
- rotor stages
- impeller rotor
- 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
Links
- 239000000919 ceramic Substances 0.000 claims abstract description 15
- 230000015572 biosynthetic process Effects 0.000 claims description 2
- 238000011109 contamination Methods 0.000 abstract 1
- 239000000463 material Substances 0.000 description 5
- 230000006835 compression Effects 0.000 description 2
- 238000007906 compression Methods 0.000 description 2
- 239000012530 fluid Substances 0.000 description 2
- XAGFODPZIPBFFR-UHFFFAOYSA-N aluminium Chemical compound [Al] XAGFODPZIPBFFR-UHFFFAOYSA-N 0.000 description 1
- 229910052782 aluminium Inorganic materials 0.000 description 1
- 239000004411 aluminium Substances 0.000 description 1
- 238000010276 construction Methods 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 230000001050 lubricating effect Effects 0.000 description 1
- 239000007787 solid Substances 0.000 description 1
Images
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.
- EP-A-0305700 discloses a compressor which may, in general terms, be described as comprising:
- the bearing means comprise 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.
- 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.
- 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.
- 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 6 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).
- an extremely efficient compressor is provided according to the invention.
- the compressor enables a compact turbomachine to be used in applications previously served mainly be 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).
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Thermal Sciences (AREA)
- Structures Of Non-Positive Displacement Pumps (AREA)
- Compressor (AREA)
Claims (10)
- Kompressor (1) umfassend:(a) eine drehbare Welle (2);(b) Antriebsmittel (7, 23) zur Drehung der Welle, wobei die Antriebsmittel einen Elektromotor umfassen, dessen Rotor (7) auf der Welle (2) gelagert ist;(c) wenigstens zwei Flügelradstufen (4, 5, 6), die auf in Längsrichtung einen Abstand voneinander aufweisenden Teilen der Welle (2) so gelagert sind, daß der Elektromotor (7, 23) zwischen den einen Abstand voneinander aufweisen Teilen angeordnet ist;(d) Zwischenkühlermittel (15, 16), die zwischen den Flügelradstufen vorgesehen sind; und(e) Lagermittel (8, 9) für die Welle;
- Kompressor nach Anspruch 1, dadurch gekennzeichnet, daß die Welle (2) mit gehärteten oder keramischen Oberflächenteilen versehen ist, mit denen die Keramik-Lagerfläche (13) der entsprechenden Kipp-Klötze (12) der Lagermittel (8, 9) zusammenwirkt.
- Kompressor nach Anspruch 1 oder 2, dadurch gekennzeichnet, daß zwei Achslager (8, 9) vorgesehen sind, um einen Abstand voneinander aufweisende Teile der Welle zu lagern, daß beide Achslager luft- oder gasgeschmierte Klotz-Lager sind, deren Lagerklötze (12) mit entsprechenden keramischen Lagerflächen (13) versehen sind.
- Kompressor nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, daß die Welle durch wenigstens ein Axial-Drucklager (10) gelagert ist.
- Kompressor nach Anspruch 4, dadurch gekennzeichnet, daß das Axial-Drucklager ein selbstwirkendes luft- oder gasgeschmiertes Klotz-Lager ist, das einen Lagerklotz (10a, 10b) aufweist, der mit einer keramischen Lagerfläche versehen ist.
- Kompressor nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, daß die Flügelradstufen (4, 5, 6) an entgegengesetzten Enden der Welle (2) fliegend angeordnet sind.
- Kompressor nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, daß mehr als zwei Flügelradstufen (4, 5, 6) vorgesehen sind.
- Kompressor nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, daß wenigstens zwei Flügelradstufen (4, 5, 6) in entgegengesetzter Formation relativ zueinander angeordnet sind, so daß das entsprechende Arbeitsgas in die jeweiligen Flügelradstufen in entgegengesetzten Richtungen fließt.
- Kompressor nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, daß Abdichtungsmittel für die Welle (2) so vorgesehen sind, daß sie einen Zugang des Arbeitsgases von den Flügelradstufen (4, 5, 6) zu dem Motor und den Lagermitteln hemmen.
- Kompressor nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, daß der Elektromotor so ausgelegt ist, daß er die Welle mit einer Geschwindigkeit von mehr als 50.000 Umdrehungen pro Minute in Drehung versetzt.
Applications Claiming Priority (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
GB929219167A GB9219167D0 (en) | 1992-09-10 | 1992-09-10 | Compressor |
GB9219167 | 1992-09-10 | ||
PCT/GB1993/001900 WO1994005913A1 (en) | 1992-09-10 | 1993-09-08 | Compressor |
Publications (2)
Publication Number | Publication Date |
---|---|
EP0667934A1 EP0667934A1 (de) | 1995-08-23 |
EP0667934B1 true EP0667934B1 (de) | 1998-04-01 |
Family
ID=10721708
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP94908821A Expired - Lifetime EP0667934B1 (de) | 1992-09-10 | 1993-09-08 | Verdichter |
Country Status (13)
Country | Link |
---|---|
EP (1) | EP0667934B1 (de) |
JP (1) | JPH08501367A (de) |
CN (1) | CN1086587A (de) |
AT (1) | ATE164662T1 (de) |
AU (1) | AU682318B2 (de) |
CA (1) | CA2144181A1 (de) |
DE (1) | DE69317791T2 (de) |
GB (1) | GB9219167D0 (de) |
IL (1) | IL106924A (de) |
MY (1) | MY109678A (de) |
RU (1) | RU2118714C1 (de) |
WO (1) | WO1994005913A1 (de) |
ZA (1) | ZA936403B (de) |
Families Citing this family (17)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
GB9404436D0 (en) * | 1994-03-08 | 1994-04-20 | Welsh Innovations Ltd | Compressor |
US5795138A (en) * | 1992-09-10 | 1998-08-18 | Gozdawa; Richard | Compressor |
FI103296B1 (fi) | 1997-12-03 | 1999-05-31 | High Speed Tech Ltd Oy | Menetelmä ylipaineisen kaasun tuottamiseksi |
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 |
WO2001052279A1 (en) | 2000-01-11 | 2001-07-19 | Gsi Lumonics Inc | Rotary device with matched expansion ceramic bearings |
EP1321680A3 (de) | 2001-12-22 | 2003-12-10 | Miscel Oy | Stömungsmaschinen-Aggregat |
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 |
CA2373905A1 (en) * | 2002-02-28 | 2003-08-28 | Ronald David Conry | Twin centrifugal compressor |
EP1353041A1 (de) * | 2002-04-12 | 2003-10-15 | ABB Turbo Systems AG | Turbolader mit Mittel auf der Welle zur axialen Sicherung der besagten Welle beim Bersten des Verdichterrades |
CN102151852B (zh) * | 2011-04-27 | 2012-06-27 | 天津大学 | 一种动静压陶瓷主轴装置 |
RU2529070C1 (ru) * | 2013-03-12 | 2014-09-27 | Федеральное Государственное Автономное Образовательное Учреждение Высшего Профессионального Образования "Дальневосточный Федеральный Университет" (Двфу) | Упорный подшипниковый узел |
RU2533948C2 (ru) * | 2013-03-12 | 2014-11-27 | 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 |
WO2015157434A1 (en) * | 2014-04-08 | 2015-10-15 | Caire Inc. | Rotary systemes lubricated by fluid being processed |
CN104967253B (zh) * | 2015-07-16 | 2018-03-30 | 莱克电气股份有限公司 | 高速无霍尔三相吸尘器电机 |
Family Cites Families (8)
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 |
US4125345A (en) * | 1974-09-20 | 1978-11-14 | Hitachi, Ltd. | Turbo-fluid device |
GB1512381A (en) * | 1975-05-06 | 1978-06-01 | Nat Res Dev | Gas compression apparatus including an axial thrust bearing |
CH663644A5 (de) * | 1982-02-22 | 1987-12-31 | Bbc Brown Boveri & Cie | Turboverdichter. |
FR2528127A1 (fr) * | 1982-06-04 | 1983-12-09 | Creusot Loire | Moto-compresseur centrifuge electrique integre a grande vitesse |
EP0297691A1 (de) * | 1987-06-11 | 1989-01-04 | Acec Energie S.A. | Motor- Kompressor-Aggregat |
DE3729486C1 (de) * | 1987-09-03 | 1988-12-15 | Gutehoffnungshuette Man | Kompressoreinheit |
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 |
-
1992
- 1992-09-10 GB GB929219167A patent/GB9219167D0/en active Pending
-
1993
- 1993-08-31 ZA ZA936403A patent/ZA936403B/xx unknown
- 1993-09-06 IL IL10692493A patent/IL106924A/en not_active IP Right Cessation
- 1993-09-08 AU AU49767/93A patent/AU682318B2/en not_active Ceased
- 1993-09-08 CA CA002144181A patent/CA2144181A1/en not_active Abandoned
- 1993-09-08 EP EP94908821A patent/EP0667934B1/de not_active Expired - Lifetime
- 1993-09-08 WO PCT/GB1993/001900 patent/WO1994005913A1/en active IP Right Grant
- 1993-09-08 RU RU95109152A patent/RU2118714C1/ru active
- 1993-09-08 AT AT94908821T patent/ATE164662T1/de not_active IP Right Cessation
- 1993-09-08 JP JP6507023A patent/JPH08501367A/ja active Pending
- 1993-09-08 DE DE69317791T patent/DE69317791T2/de not_active Expired - Fee Related
- 1993-09-09 MY MYPI93001842A patent/MY109678A/en unknown
- 1993-09-10 CN CN93117463A patent/CN1086587A/zh active Pending
Also Published As
Publication number | Publication date |
---|---|
JPH08501367A (ja) | 1996-02-13 |
MY109678A (en) | 1997-04-30 |
CA2144181A1 (en) | 1994-03-17 |
DE69317791D1 (de) | 1998-05-07 |
AU4976793A (en) | 1994-03-29 |
GB9219167D0 (en) | 1992-10-28 |
ATE164662T1 (de) | 1998-04-15 |
WO1994005913A1 (en) | 1994-03-17 |
RU2118714C1 (ru) | 1998-09-10 |
IL106924A (en) | 1996-10-16 |
CN1086587A (zh) | 1994-05-11 |
RU95109152A (ru) | 1997-02-20 |
DE69317791T2 (de) | 1998-12-10 |
ZA936403B (en) | 1994-08-08 |
EP0667934A1 (de) | 1995-08-23 |
IL106924A0 (en) | 1993-12-28 |
AU682318B2 (en) | 1997-10-02 |
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