EP1604115B1 - Gruppe von integrierten zentrifugalkompressoren - Google Patents

Gruppe von integrierten zentrifugalkompressoren Download PDF

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Publication number
EP1604115B1
EP1604115B1 EP03727579.9A EP03727579A EP1604115B1 EP 1604115 B1 EP1604115 B1 EP 1604115B1 EP 03727579 A EP03727579 A EP 03727579A EP 1604115 B1 EP1604115 B1 EP 1604115B1
Authority
EP
European Patent Office
Prior art keywords
compressor unit
compressor
casing
unit according
motor
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
EP03727579.9A
Other languages
English (en)
French (fr)
Other versions
EP1604115B8 (de
EP1604115A1 (de
Inventor
Pierre Laboube
Jean-Marc Pugnet
Patrick Friez
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.)
Thermodyn SAS
Original Assignee
Thermodyn SAS
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 Thermodyn SAS filed Critical Thermodyn SAS
Priority to SI200332488A priority Critical patent/SI1604115T1/sl
Publication of EP1604115A1 publication Critical patent/EP1604115A1/de
Publication of EP1604115B1 publication Critical patent/EP1604115B1/de
Application granted granted Critical
Publication of EP1604115B8 publication Critical patent/EP1604115B8/de
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
    • F04D29/05—Shafts or bearings, or assemblies thereof, specially adapted for elastic fluid pumps
    • F04D29/056—Bearings
    • F04D29/058—Bearings magnetic; electromagnetic
    • 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
    • F04D17/125—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 the casing being vertically split
    • 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
    • F04D25/022—Units comprising pumps and their driving means comprising a yielding coupling, e.g. hydraulic
    • 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
    • F04D29/053—Shafts
    • F04D29/054—Arrangements for joining or assembling shafts

Definitions

  • the invention relates to a turbocharger or motor-compressor and, in particular, an integrated motor-compressor unit, as disclosed in the documents US4969803 and US6464469 B1 .
  • the integrated motor-compressor units comprise a sealed common housing 10, in which are placed an electric motor 12 and a compressor unit 14, for example multi-stage, which comprises a set of paddle wheels, such as 16, carried by a shaft 18.
  • the motor 12 rotates a rotor 20, this rotor 20 being coupled to the shaft 18 of the compressor 14 via a rigid coupling 22.
  • Bearings 24, 26 and 28 are used to support the line of trees of the motor-compressor unit.
  • the assembly is placed in a common housing 29.
  • the gas to be handled is presented at the inlet E of the turbocharger and is then transmitted to the successive compression stages of the compressor unit to be delivered at the output S.
  • An axial bearing 30 is used to prevent the axial displacement of the compressor 14 during its operation. .
  • This type of arrangement has the advantage of considerably simplifying the shaft line of the compressor unit since the assembly consisting of the motor, its rotor and its end bearings, as well as by the rigid coupling. and by the axial stop, are located inside the housing and are subjected to the pressure of the gas admitted to the inlet of the first compression stage.
  • the object of the invention is therefore to overcome these disadvantages.
  • the invention therefore relates to a centrifugal compressor unit comprising a motor, at least one compressor comprising a driven shaft driven by the motor rotor and an assembly of at least two impellers mounted on the driven shaft, the assembly consisting of the motor and the compressor being mounted in a gas-tight common housing operated by the compressor unit.
  • the rotor and the driven shaft are connected by a flexible coupling disposed in the housing.
  • the casing comprises a plurality of casing elements joined together in leaktight manner, each casing element enclosing the motor or a compressor.
  • the housing is provided with an orifice formed between the adjacent housing elements for access to the flexible coupling, said orifice being provided with sealing means.
  • the flexible coupling includes a diaphragm or flexible blade coupling, or a torsion shaft coupling.
  • each end of the driven shaft and the rotor is supported by an end bearing, which can be secured to the housing.
  • the end bearings are radial magnetic bearings.
  • the compressor unit comprises an axial abutment on which the shaft rests driven compressor, during operation of the turbocharger.
  • This stop is for example a magnetic stop.
  • a motor-compressor essentially comprises an electric motor 34 with a high rotation speed (6000 to 16 000 rpm) powered by a frequency converter and comprising a stator 36 and a rotor 38 supported by two end bearings 40 and 42, and a compressor unit 44 having a set of impeller wheels 46, 48, 50 and 52, mounted on a driven shaft 54.
  • the assembly is mounted on a pedestal (not shown) and is disposed in a housing 55 common gas-tight handled by the turbocharger.
  • the motor-compressor unit 44 may comprise any number of such impellers, or, as will be described later, comprise another arrangement of the impeller wheels.
  • the housing is composed of an assembly of integral housing elements such as 55a and 55b, each providing support and protection of the motor or a compression stage, and secured by appropriate fastening means.
  • the compressor shaft 44 is journalled in bearings 55 and 56.
  • a gas inlet port 58 in the turbocharger 32 formed in the casing opens out at the first compression stage, constituted by the paddle wheel designated by FIG. reference 46, while an outlet port 60 recovers the gas handled by the turbocharger, at the outlet of the last compression stage constituted by the impeller designated by the reference numeral 52, as designated by the arrows F.
  • an axial stop 62 integral with the driven shaft is disposed between two fixed bearings 66 and 68, so as to limit the axial overshoot of the driven shaft 54 compressor stage 44, together with an axial aerodynamic balancing piston 70.
  • a flexible coupling 72 couples the rotor 38 of the motor 34 and the driven shaft 54 of the compressor stage 44.
  • a coupling 72 can be made either from a diaphragm-type coupling or from a flexible blade-type coupling, or a torsion-shaft type coupling.
  • any other type of flexible coupling suitable for the intended use may be used. It should be noted, however, that the use of a torsion-shaft-type coupling makes it possible to reduce ventilation losses, to reduce the level of noise generated, and to propagate more easily the axial thrust provided by the motor.
  • the housing is provided with an orifice 76 which opens out opposite the junction zone between the rotor 38 and the driven shaft 54.
  • This orifice is associated with a removable sealing device 78
  • the entire interior of the turbocharger is bathed by the process gas handled by the compressor, including the flexible coupling 72.
  • the internal volume of the turbocharger has no shaft outlet seal, but only rotary joints 80 which are subjected to small pressure differences, such as labyrinth type rotary joints which serve for the operation of the compressor.
  • the engine is left at the suction pressure of the compressor, and a flow of gas is organized to ensure its cooling.
  • the radial bearings 40, 42, 55 and 56 used for supporting the rotors do not require a supply of lubricating fluid.
  • these bearings are controlled so that they adapt to the dynamic behavior of the rotor or the driven shaft 54 which they provide support, that is to say generally rigid on the motor side and generally flexible on the driven shaft side.
  • the bearings 40, 42, 55 and 56 are fixed rigidly relative to the housing. These forces are constituted by the radial forces of weight, the dynamic radial forces related to the residual unbalances, and the axial forces due to the resultant aerodynamic thrust on the stages of compression. These bearings also allow a radial displacement of the rotor or the driven shaft which they provide support, to enable lineation of these elements of the shaft line during maintenance phases.
  • the casing is constituted by an assembly of casing elements respectively providing support for the motor and the compression stage, these casing elements being rigidly and sealingly associated.
  • the ends mutually opposite sides 82 and 84 of the casing thus formed are closed, on the one hand by a bolted bottom 86, on which are fixed the bearings 40 of the rotor 38 and, on the other hand, by a second bottom 88 which supports the bearing 56 in which the driven shaft 54 and the balancing piston 70, which is fixed on the housing, for example by means of shear rings 90, is journalled.
  • the invention which has just been described, which uses an electric motor and a compressor unit arranged in a sealed common housing and whose shafts respectively driving and driven are secured by means of a flexible coupling disposed in the gas handled by the turbocharger, has several advantages.
  • each of the rotors, engine and compressor unit retains the vibratory behavior of its own.
  • the motor rotor is generally of rigid type, with the first critical bending speed above the speed of rotation.
  • the compressor rotor is generally of flexible type, with the first critical bending speed below the maximum rotational speed. In this way, it is not possible to create specific modes of bending coupled between the two rotors which, during operation, may develop hot spots on the rotor of the motor, constituting thermal imbalances of phase and of uncontrollable amplitude.
  • the presence of a flexible coupling also facilitates the positioning of the first natural torsional frequency, and also contributes to reducing the stress in the compressor shaft end in the event of an electrical short-circuit at the motor terminals.
  • the flexible coupling can be uncoupled from the orifice 76 passing through the housing, and each of the rotor and driven shaft can be extracted while the other continues to be supported by its two levels. In this way, the rotor and driven shaft are protected during this operation, the reassembly is much faster and lineage and dynamic balancing facilitated, because of the access to the two central planes on each end of tree.
  • the compressor unit 44 is arranged so that the entire rotor-diaphragm assembly can be pulled from the body at the same time as the bottom 88, without having to separate the casing from its base and the pipework. process gas. It will be noted that, during these assembly-disassembly phases, the rotors rest on their respective bearings without risk of damage to the rotating parts as well as stator parts which could otherwise come into contact with the rotors during these operations.
  • turbocharger equipped with a multi-stage compressor integrated in line with a single compression section and four stages
  • the invention is also applicable to other types of motor-compressors, for example to two sections S1 and S2 in line, for example two stages each, ensuring each compression of a process gas with, for example, intermediate cooling.
  • two inputs E'1 and E'2 and two outputs S'1 and S'2 opposite the input and output of each of these sections are provided in the housing ( figure 3 ).
  • the first compression stage of one of the sections S2 may be arranged facing the second compression stage of the other section S1.
  • the first compression stages of each of sections S1 and S2 may be arranged side by side.
  • the pressure prevailing in the engine will be that of suction on the low pressure side.
  • each of the compression bodies prefferably have gas extraction means or reinjection devices, which then considerably increases the number of combinations of possible arrangements.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Electromagnetism (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
  • Supercharger (AREA)
  • Medicines Containing Plant Substances (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
  • Rotary Pumps (AREA)

Claims (9)

  1. Kreiselverdichtereinheit, die einen Motor (34), mindestens einen Verdichter (44; 44`, 44") mit einer angetriebenen Welle (54; 54`, 54"), die vom Rotor (38) des Motors angetrieben wird, und eine Anordnung von an der angetriebenen Welle befestigten Laufrädern umfasst, wobei die Anordnung aus dem Motor und dem Verdichter an einem gemeinsamen Gehäuse (55), das gegenüber von der Verdichtereinheit verwendetem Gas dicht ist, befestigt ist, dadurch gekennzeichnet, dass der Rotor und die angetriebene Welle durch ein in dem Gehäuse angeordnetes flexibles Verbindungsstück (72; 72', 72") verbunden sind.
  2. Verdichtereinheit nach Anspruch 1, dadurch gekennzeichnet, dass das Gehäuse mehrere Gehäuseelemente (55a, 55b) umfasst, die abdichtend fest miteinander verbunden sind, wobei jedes Gehäuseelement den Motor oder einen Verdichter umgibt.
  3. Verdichtereinheit nach Anspruch 2, dadurch gekennzeichnet, dass das Gehäuse mit einer Öffnung (76) versehen ist, die zwischen den nebeneinanderliegenden Gehäuseelementen zum Zugang zum flexiblen Verbindungsstück vorgesehen ist, wobei die Öffnung mit Mitteln (78) zum dichten Verschließen versehen ist.
  4. Verdichtereinheit nach einem der Ansprüche 1-3, dadurch gekennzeichnet, dass das flexible Verbindungsstück (72, 72', 72") ein Element umfasst, das unter einem Verbindungsstück aus einer Membran, einem Verbindungsstück aus einer flexiblen Lage und einem Verbindungsstück aus einer torsionselastischen Welle ausgewählt ist.
  5. Verdichtereinheit nach einem der Ansprüche 1-4, dadurch gekennzeichnet, dass jedes Ende der angetriebenen Welle und des Rotors durch ein Endlager (40, 42, 55, 56) gestützt wird.
  6. Verdichtereinheit nach Anspruch 5, dadurch gekennzeichnet, dass jedes Endlager (40, 42, 55, 56) fest mit dem Gehäuse verbunden ist.
  7. Verdichtereinheit nach einem der Ansprüche 5 und 6, dadurch gekennzeichnet, dass die Endlager magnetische Radiallager sind.
  8. Verdichtereinheit nach einem der Ansprüche 1-7, dadurch gekennzeichnet, dass sie ein axiales Drucklager (62) umfasst, an dem die angetriebene Welle des Verdichters beim Betrieb des Turboladers anliegt.
  9. Verdichtereinheit nach Anspruch 8, dadurch gekennzeichnet, dass es sich bei dem axialen Drucklager (62) um ein magnetisches Drucklager handelt.
EP03727579.9A 2003-03-10 2003-03-10 Gruppe von integrierten zentrifugalkompressoren Expired - Lifetime EP1604115B8 (de)

Priority Applications (1)

Application Number Priority Date Filing Date Title
SI200332488A SI1604115T1 (sl) 2003-03-10 2003-03-10 Enota centrifugalnih kompresorjev

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/FR2003/000768 WO2004083644A1 (fr) 2003-03-10 2003-03-10 Groupe compresseur centrifuge

Publications (3)

Publication Number Publication Date
EP1604115A1 EP1604115A1 (de) 2005-12-14
EP1604115B1 true EP1604115B1 (de) 2016-05-11
EP1604115B8 EP1604115B8 (de) 2016-07-13

Family

ID=32982116

Family Applications (1)

Application Number Title Priority Date Filing Date
EP03727579.9A Expired - Lifetime EP1604115B8 (de) 2003-03-10 2003-03-10 Gruppe von integrierten zentrifugalkompressoren

Country Status (9)

Country Link
US (1) US7144226B2 (de)
EP (1) EP1604115B8 (de)
AU (1) AU2003233369A1 (de)
CY (1) CY1117875T1 (de)
ES (1) ES2586658T3 (de)
HU (1) HUE029908T2 (de)
NO (1) NO339342B1 (de)
SI (1) SI1604115T1 (de)
WO (1) WO2004083644A1 (de)

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FR1430986A (fr) * 1965-01-22 1966-03-11 Hispano Suiza Sa Perfectionnements apportés aux appareils à rotor entraîné mécaniquement à partir d'un relais de puissance
US3942908A (en) * 1974-05-03 1976-03-09 Norwalk-Turbo, Inc. Gas turbine driven high speed centrifugal compressor unit
JPH076518B2 (ja) * 1987-07-23 1995-01-30 三菱重工業株式会社 遠心圧縮機
DE3729486C1 (de) * 1987-09-03 1988-12-15 Gutehoffnungshuette Man Kompressoreinheit
RO111492B1 (ro) * 1995-12-21 2003-08-29 Comoti S.A. Compresor centrifugal cu multiplicator încorporat
KR100288315B1 (ko) * 1999-03-15 2001-04-16 김평길 2단 원심압축기
EP1074746B1 (de) * 1999-07-16 2005-05-18 Man Turbo Ag Turboverdichter
US6551191B2 (en) * 2000-09-22 2003-04-22 Man Turbomaschinen Ag Coupling apparatus

Also Published As

Publication number Publication date
EP1604115B8 (de) 2016-07-13
HUE029908T2 (hu) 2017-04-28
US7144226B2 (en) 2006-12-05
NO20054198D0 (no) 2005-09-09
WO2004083644A1 (fr) 2004-09-30
US20040179961A1 (en) 2004-09-16
AU2003233369A1 (en) 2004-10-11
ES2586658T3 (es) 2016-10-18
CY1117875T1 (el) 2017-05-17
EP1604115A1 (de) 2005-12-14
NO339342B1 (no) 2016-11-28
NO20054198L (no) 2005-10-07
SI1604115T1 (sl) 2016-10-28

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