WO2019199321A1 - Compresseur centrifuge avec roue sans arbre - Google Patents

Compresseur centrifuge avec roue sans arbre Download PDF

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Publication number
WO2019199321A1
WO2019199321A1 PCT/US2018/027507 US2018027507W WO2019199321A1 WO 2019199321 A1 WO2019199321 A1 WO 2019199321A1 US 2018027507 W US2018027507 W US 2018027507W WO 2019199321 A1 WO2019199321 A1 WO 2019199321A1
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WO
WIPO (PCT)
Prior art keywords
journal
impeller
hub
compressor
coupled
Prior art date
Application number
PCT/US2018/027507
Other languages
English (en)
Inventor
Byron L. Mohr
Edward Kunkel
Original Assignee
Dresser-Rand Company
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 Dresser-Rand Company filed Critical Dresser-Rand Company
Priority to PCT/US2018/027507 priority Critical patent/WO2019199321A1/fr
Publication of WO2019199321A1 publication Critical patent/WO2019199321A1/fr

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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
    • 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
    • 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
    • F04D25/0613—Units comprising pumps and their driving means the pump being electrically driven the electric motor being specially adapted for integration in the pump the electric motor being of the inside-out type, i.e. the rotor is arranged radially outside a central stator
    • 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

Definitions

  • the invention relates to centrifugal compressors. More particularly, the invention relates to shaftless impeller mounting in centrifugal compressors, where the impeller supported and positioned by a journal and rotates on magnetic bearings interposed between the journal and an impeller hub.
  • the impeller is driven by an electric motor, whose stator is embedded in the journal and whose rotor is embedded in the impeller hub.
  • Centrifugal compressors typically incorporate a shaft-mounted impeller in the compressor casing or housing.
  • the impeller is rigidly affixed to the compressor shaft; the shaft provides multiple mechanical functions.
  • Second, the shaft rotates the impeller with a driver, such as an electric motor or an engine.
  • the compressor shaft is in turn rotationally mounted in the compressor housing by bearings that are axially offset from the impeller, so that it can support and rotate the impeller.
  • Some known compressors have“center-mounted” impellers, where ends of the compressor shaft extend from both axial ends of the impeller hub, and are supported in film-lubricated, rolling element or magnetic bearings.
  • Shafts with offset bearing mounts require use of compressor casings of sufficient axial length to retain one or more shaft-mounted impellers and the associated bearings/bearing mounts. These shafts require sufficient cross-sectional area and strength to resist shear and bending stresses associated with the axially offset impeller loads and their bearing supports.
  • Exemplary embodiments of centrifugal compressors described herein comprise shaftless impellers, rotatively mounted on journals.
  • the journal is stationary.
  • the journal is incorporated within a stationary journal shaft that extends axially from both axial ends of the impeller. Both ends of the journal shaft are coupled to the compressor casing.
  • the journal is a journal stub, one end of which is coupled to compressor casing and the other end of which projects into at least one of the axial ends of the impeller hub, in cantilever-like fashion.
  • a pair of opposed, first and second journal stubs project respectively from a shroud side of the casing into a first axial end of the impeller hub, and from a hub side of the casing into a second axial end of the impeller hub.
  • One or more magnetic bearings are interposed between the journal and a hollow hub of the impeller. The journal and magnetic bearing support and position the impeller within an impeller cavity of the compressor casing.
  • first and second, opposing, magnetically repulsing portions of the magnetic bearing are embedded in the journal and the impeller hub, respectively.
  • permanent magnets or electromagnetic coils are embedded in the impeller hub, and opposing permanent magnets or electromagnetic coils are embedded in the journal.
  • the impeller is rotated with a driver, in order to compress working fluids flowing through the compressor.
  • a drive shaft which is independent of the journal, is coupled to the impeller and rotates the impeller about the journal shaft.
  • respective permanent magnets or electromagnetic coils of a drive motor are embedded in the impeller hub and the opposing journal, eliminating the need for an external impeller drive.
  • Other exemplary embodiments of the invention feature a compressor, having a compressor casing that defines a casing longitudinal axis. An impeller cavity circumscribes the casing’s longitudinal axis.
  • a journal is disposed within the casing; it defines a journal central axis that is congruent with the casing longitudinal axis.
  • An impeller is disposed within and is circumscribed by the impeller cavity.
  • the impeller has a hollow hub that is concentrically aligned with, and configured to rotate about the journal central axis.
  • a magnetic bearing is interposed between the journal and the hollow hub, for supporting and positioning the impeller within the impeller cavity radially relative to the journal central axis.
  • Additional exemplary embodiments of the invention feature a method for aligning and supporting a rotatable impeller in a compressor, having a hollow hub.
  • the impeller is supported by interposing a magnetic bearing in the hollow hub.
  • the magnetic bearing circumscribes a stationary journal disposed within an impeller cavity of a compressor casing.
  • the stationary journal defines a journal central axis that is congruent with a casing longitudinal axis; both axes circumscribed by the impeller cavity.
  • At least one electromagnet of the magnetic bearing is energized. This generates a repulsive magnetic field in the bearing that radially and/or axially positions the journal and hub relative to each other along the journal central axis.
  • Selectively energizing the at least one electromagnet aligns the impeller and the stationary journal relative to each other by varying energization of the electromagnet.
  • FIG. 1 is an axial cross-sectional, schematic view of a centrifugal compressor, in accordance with an embodiment described herein, where the impeller is rotatively mounted on a stationary journal shaft;
  • FIG. 2 is an axial cross-sectional, schematic view of a centrifugal compressor, in accordance with an embodiment described herein, where the impeller is rotatively mounted on a stationary journal stub that is coupled to the shroud side of the compressor casing;
  • FIG. 3 is an axial cross-sectional, schematic view of a centrifugal compressor, in accordance with an embodiment described herein, where the impeller is rotatively mounted on a stationary journal stub that is coupled to the hub side of the compressor casing;
  • FIG. 4 is an axial cross-sectional, schematic view of a centrifugal compressor, in accordance with an embodiment described herein, where the impeller is rotatively mounted on a pair of opposed, axially spaced, stationary first and second journal stubs, which are respectively coupled to the shroud side, and the hub side of the compressor casing, and driven by a drive shaft that is independent of the journal stubs;
  • FIG. 5 is an axial cross-sectional, schematic view of a centrifugal compressor, in accordance with an embodiment described herein, where a plurality of axially spaced impellers are disposed within and circumscribed by the impeller cavity; each impeller respectively having a hollow hub concentrically aligned with, and configured to rotate about the journal central axis of a stationary journal shaft;
  • FIG. 6 is a fragmented, axial cross-sectional, schematic view of a centrifugal compressor, in accordance with an embodiment described herein, where opposed portions of the magnetic bearing respectively is embedded within the journal and the impeller hub;
  • FIG. 7 is an axial cross-sectional, schematic view of an impeller, in accordance with an embodiment described herein, an electromagnetic coil of an electromagnetic bearing is embedded in the impeller hub;
  • FIG. 8 is a plan view schematic of a journal that incorporates embedded electromagnetic coils for radial support, electromagnetic bearings, and for a stator of an embedded drive motor, in accordance with an embodiment described herein;
  • FIG. 9 is a plan view schematic of a journal that incorporates embedded electromagnetic coils for electromagnetic thrust and radial support bearings, and for a stator of an embedded drive motor, in accordance with an embodiment described herein.
  • Exemplary embodiments of centrifugal compressors described herein comprise shaftless impellers, rotatively mounted on journals.
  • the journal is stationary.
  • a drive shaft which is independent of the journal, is coupled to the impeller and rotates the impeller about the journal shaft.
  • the journal is incorporated within a stationary journal shaft that extends axially from both axial ends of the impeller. Both ends of the journal shaft are coupled to the compressor casing.
  • the journal is a journal stub, one end of which is coupled to compressor casing and the other end of which projects into at least one of the axial ends of the impeller hub, in cantilever-like fashion.
  • a pair of opposed, first and second journal stubs project respectively from a shroud side of the casing into a first axial end of the impeller hub, and from a hub side of the casing into a second axial end of the impeller hub.
  • One or more magnetic bearings are interposed between the journal and a hollow hub of the impeller.
  • the journal and magnetic bearing support and position the impeller within an impeller cavity of the compressor casing.
  • the journals, magnetic bearings and the impeller hub interfaces support the impeller rotatively within compressor casing.
  • the impeller is driven rotatively by a driver, to compress a working fluid flowing through the compressor.
  • a drive shaft that is independent of the journal or journals rotates the impeller.
  • the impeller is directly driven by a motor whose respective rotor and stator permanent magnets and/or electromagnetic coils are directly embedded within the journal and impeller hub.
  • FIG. 1 shows, schematically, a fragmentary view of a compressor 20, having a compressor casing 22.
  • the compressor casing 22 is split vertically into a shroud side 24 and a hub side 26 with a diffuser channel 36.
  • the casing is split horizontally into upper and lower halves along a casing longitudinal axis 28.
  • An impeller cavity 30 within the casing circumscribes the casing longitudinal axis 28.
  • Process fluid F enters the impeller cavity 30, via an inlet 31, and flows there through, within a path bounded by a shroud surface 32 and a hub surface 34 of the compressor casing 22, and exits via a diffuser 36 (not shown).
  • a journal 40, having an outer surface 42 is disposed within the casing 28.
  • the journal outer surface 42 is concentric with a journal central axis 44 that is congruent with the casing longitudinal axis 28.
  • An impeller 50 is disposed within and circumscribed by the impeller cavity 30.
  • the impeller 50 has a hollow hub 52 that is concentrically aligned with, and configured to rotate about the journal central axis 44.
  • a magnetic bearing 60 is interposed between the journal 40 and the hollow hub 52, for supporting and positioning the impeller 50 within the impeller cavity 30 radially relative to the journal central axis 44.
  • the magnetic bearing has a first portion 62 that is retained within or otherwise coupled to the hub 52 and a second portion 64 that is coupled to the outer surface 42 of the journal 40.
  • the journal 40 is part of a journal shaft that extends axially through both axial ends of the impeller hub 52 coupled to both the shroud side 24 and the hub side 26 of the compressor casing 22.
  • the journal 40 is stationary and does not rotate within the compressor casing 22. In other embodiments, the journal is free to rotate within the compressor casing 22.
  • FIGs. 2-6 show other impeller-supporting journal, impeller hub, and magnetic bearing embodiments for centrifugal compressors. Impeller rotation and acceleration of process fluid F through these compressor embodiments is functionally equivalent to the compressor 20 of FIG. 1.
  • the compressor 70 has a compressor casing 72 with shroud side 74 of the casing defining a casing longitudinal axis 76 and an impeller cavity 78.
  • a journal stub 80 has a first end 82 that is coupled to the shroud side 74 of the casing 72, and a second end 84 projecting away from the shroud side in cantilever-like fashion, and an outer surface 86.
  • the impeller 88 has an impeller hub 90.
  • a shroud-side axial end 92 of the inner annular surface of the impeller hub 90 receives the second end 84 of the journal stub 80.
  • the journal stub 80 projects through both axial ends of the impeller hub 90 (not shown).
  • a magnetic bearing 94 is interposed between the inner annular surface of the impeller hub 90 hub and the outer surface 86 of the journal stub 80.
  • the compressor 100 has a compressor casing 102 with hub side 104 of the casing defining a casing longitudinal axis 108 and an impeller cavity 110.
  • a journal stub 112 has a first end 114 that is coupled to the hub side 104 of the casing 102, and a second end 116 projecting away from the hub side in cantilever-like fashion, and an outer surface 118.
  • the impeller 120 has an impeller hub 122.
  • a hub- side axial end 124 of the inner annular surface of the impeller hub 122 receives the second end 116 of the journal stub 112.
  • the journal stub 112 projects through both axial ends of the impeller hub 122 (not shown).
  • the compressor 130 of FIG. 4 has a compressor casing 132, with a shroud side 134, a hub side 136, and a casing longitudinal axis 138.
  • An impeller cavity 140 within the casing 132 circumscribes the casing longitudinal axis 138.
  • the compressor 130 has a pair of opposed, mutually spaced, concentrically aligned first 142 and second 146 journal stubs.
  • the first journal stub 142 has a first end 143 coupled to the shroud side 134 of the casing 132; it defines a first hollow cavity 144 and a distal end 145.
  • the second journal stub 146 has a first end 147 coupled to the hub side 136 of the casing 132; it defines a and second hollow cavity 148 and a distal end 149.
  • the impeller 156 has an impeller hub 158 that straddles the opposed, respective distal ends 145 and 149 of the first 142 and second 146 journal stubs.
  • a first magnetic bearing 160 is interposed between the inner annular surface of the impeller hub 158 on its shroud end 164 and the first journal stub 142.
  • a second magnetic bearing 162 is interposed between the inner annular surface of the hub 158 on its hub end 166 and the second journal stub 146.
  • the impeller 156 is supported by, and rotates about, the respective first 142 and second 146 journal stubs and the respective first 160 and second 162 magnetic bearings.
  • the impeller-supporting journal, impeller hub, and magnetic bearing embodiments for centrifugal compressors support and align the rotating impeller radially and/or axially relative to the journal central axis, but they do not impart driving torque on the impeller.
  • the impellers are driven by drive systems that are independent from the journal/impeller hub/magnetic bearing interface.
  • a drive shaft 150 and a driver 151 e.g., an electric motor or a gas turbine engine
  • a driver 151 are coupled to and rotate the impeller 156 independent of the first 142 and second 146 stationary journal stubs.
  • the drive shaft 150 passes through the respective first 144 and second 148 hollow cavities of the first 142 and second 146 stationary journal stubs, where it mates to the impeller hub 158 via a flanged, drive shaft coupling 152.
  • a multi-stage compressor 170 is driven by a drive shaft 186 and a driver 188 (e.g., an electric motor or a gas turbine engine) that are coupled to and rotate an impeller stack 176, independent of the stationary journal shaft 174.
  • a driver 188 e.g., an electric motor or a gas turbine engine
  • a compressor casing 172 or a plurality of coupled compressor casings that are axially aligned, retains a journal shaft 174 that extends axially through and projecting from both ends of an impeller stack 176.
  • This journal shaft 174 and impeller stack 176 construction is similar to the single-stage compressor 20 construction of FIG. 1.
  • Each of the respective impellers 176A-C in the impeller stack 176 is circumscribed by its own impeller cavity (not shown).
  • One or more impeller cavities are defined in a common compressor casing, or distributed among separate, coupled compressor casings.
  • Each of the respective impellers 176A-C incorporates a respective impeller hub 178A-C.
  • Respective magnetic bearings 180A-C are interposed between the stationary journal shaft 174 and its respective hollow impeller hub 178A-C, for supporting and positioning the plurality of impellers within the impeller cavity of the compressor casing 172, radially relative to the journal central axis 185.
  • One or more tie rods 182 rigidly couple the impeller hubs 178A-C axially and radially relative to each other, to form the unitized impeller stack 176.
  • a plurality of tie rods 182 is circumferentially spaced about the respective impeller hubs 178A-C.
  • One of the axial ends of the tie rods 182 are coupled to a tie rod flange 184, which is in turn, coupled to the drive shaft 186 and the drive 188.
  • a central axis 190 of the drive shaft 186 is congruent with the journal central axis 185, but in other embodiments, those respective axes are not congruent— for example, when a gearbox is interposed between the tie rod flange 184 and the drive 188.
  • three impellers are shown in FIG. 5, other embodiments of multi-stage compressors comprise two or more than three impellers.
  • the multi-stage compressor 170 has a journal shaft 174 that passes through both axial ends of the impeller stack 176 and projects axially there from; both projecting axial ends of the journal shaft 174 are coupled to the compressor casing 172.
  • the journal shaft 174 is replaced by a journal stub, similar to any of the journal stubs 80, 112, 142, 146 of FIGs. 2-4.
  • FIGs. 1-5 incorporate magnetic bearings 60, 94, 126, 160, 162, and 180A-C.
  • the bearing 60 of FIG. 1 has a first portion 62 coupled to the impeller hub 52 and an opposed, second portion 64 coupled to the journal 40.
  • a repulsive magnetic field generated between the first 62 and second 64 portions of the magnetic bearing 60 orients the impeller hub 52 in the impeller cavity 30 in a single radial and/or axial position, relative to the journal central axis 44 and the congruently aligned, casing longitudinal axis 28.
  • the repulsive magnetic field is generated in the magnetic bearing 60 by pairs of permanent magnets, or pairs of electromagnets, or a pairing of an electromagnet and a permanent magnet.
  • Various compressor embodiments of FIGs. also 2-5 incorporate magnetic bearings 94, 126, 160, 162, and 180A-C, which have first and second portions that generate respective, repulsive magnetic fields.
  • the compressor 200 has a compressor casing 202, with a shroud side casing 204 and a hub side casing 206 that collectively define a casing longitudinal axis 208.
  • Journal shaft 210 has an outer surface 212 and an annular recess 214.
  • a centrifugal impeller 220, with an impeller hub 222 circumscribes the journal shaft 210.
  • the impeller hub 222 defines an internal annular recess 224.
  • a magnetic bearing 230 is interposed between the journal shaft 210 and the impeller hub 222, for orienting the impeller hub in a single axial position, relative to the journal central axis 208 and the congruently aligned, casing longitudinal axis 208.
  • a first portion 232 of the magnetic bearing 230 is retained within the annular recess 224 of the impeller hub 222 and a second portion 234 of the magnetic bearing is retained within the annular recess 214 of the journal shaft 210.
  • the first portion 232 of the magnetic bearing is a permanent magnet.
  • the second portion 234 of the magnetic bearing is an electromagnet whose conductive coils (not shown) are within the annular recess 214.
  • Coil leads 236 and 238 feed current from a power source 240.
  • Controller 242 regulates power supplied to the coils in the second portion 234 of magnetic bearing 230; this selectively varies the repulsive magnetic field generated between the first 232 and second 234 portions of the magnetic bearing.
  • the electromagnetic bearing power source 240 and the controller 242 are of known construction.
  • the controller 242 incorporates a processor 244 accesses and executes a non-transient instruction set, resident in software modules that are stored in a non volatile memory device 246.
  • a processor 244 accesses and executes a non-transient instruction set, resident in software modules that are stored in a non volatile memory device 246.
  • exemplary embodiments of the invention may be implemented in various forms of hardware, software, firmware, special purpose processors, or a combination thereof.
  • aspects of the invention embodiments are implemented in software as a program tangibly embodied on the program-storage memory device 246.
  • the program may be uploaded to, and executed by, a machine comprising any suitable architecture.
  • the machine is implemented on a computer platform having hardware such as one or more central processing units (CPU), a random access memory (RAM), and input/output (I/O) interface(s).
  • the computer platform also includes an operating system and microinstruction code.
  • the various processes and functions described herein may be either part of the microinstruction code or part of the program (or combination thereof) which is executed via the operating system.
  • various other peripheral devices may be connected to the computer/controller platform.
  • the shrouded impeller 250 has an impeller hub 252 with an impeller recess 254.
  • a first portion 256 of an electromagnetic bearing, including its electromagnetic coils 258 are embedded in the impeller recess 254.
  • Coil leads 260 and 262 feed current from the power source 240.
  • the controller 242 regulates power supplied to the coils 258.
  • conductive coils of electromagnetic bearings are embedded within recesses formed within the journal; some embodiments also have conductive coils embedded within the hub.
  • journal shafts 270 and 310 are shown in fragmentary elevational view. Their respective hubs 290 and 330 and their respective, related structures are shown in dashed line phantom view, but they are substantially similar to those of FIGs. 1-7. Electromagnetic bearings in FIGs. 8 and 9 function as those in the embodiments described in FIGs. 6 and 7.
  • compressor 268 has a stationary journal shaft 270 that extends axially into both axial ends of an impeller hub 290, similar to the construction shown in FIG. 1.
  • the journal extends only into one of the first and/or second axial end of the impeller hub, in cantilever-like fashion, similar to the constructions shown in FIGs. 2-4.
  • the stationary journal shaft 270 is incorporated into a multi-stage compressor, such as the one shown in FIG. 5.
  • An outer surface 272 of the journal shaft incorporates recesses 274, 276, 278 and 280.
  • Respective conductive coils 282A-C of a first electromagnetic journal bearing is wound about a projecting stub formed between the recesses 274 and 276.
  • Respective coils 284 A-C of a second electromagnetic journal bearing are wound about projecting stub formed between the recesses 278 and 280, axially offset from the coils 282A-C of the first electromagnetic bearing.
  • the hub 290 incorporates coils of a first electromagnetic hub bearing 292 and a second electromagnetic hub bearing 294 in opposed axial and radial relationship, respectively with the corresponding coils 282A- C of the first electromagnetic journal bearing and the corresponding coils 284A-C of the second electromagnetic journal bearing.
  • the compressor 308 of FIG. 9 incorporates electromagnetic thrust bearings to support axial loads imparted on its impeller.
  • Journal shaft 310 incorporates opposed orientation, frusto-conical profile, first 314 and second 316 annular surfaces, separated by the cylindrical surface 312.
  • the hub 330 incorporates opposing, female, frusto-conical profile first 334 and second 338 annular surfaces.
  • the electromagnetic coils similar to those of FIG. 8 are embedded within recesses on the opposing frusto- conical surfaces. When the coils are energized (such as by the power source 240 and controller 242 of FIG. 6), they generate repulsive electromagnetic forces FR in the radial direction and FA in the axial direction.
  • the bearings in the journal shaft 310 and the hub 330 are also thrust bearings; they eliminate the need for a separate balancing piston assembly.
  • Other embodiments incorporate other profiles of thrust bearing surfaces that generate the electromagnetic repulsive forces FR in the radial direction and FA in the axial direction.
  • Respective conductive coils 326A-C of a first electromagnetic journal bearing is wound about a projecting stub formed between the recesses 318 and 320.
  • Respective coils 328 A-C of a second electromagnetic journal bearing are wound about projecting stub formed between the recesses 322 and 324.
  • the hub 330 incorporates coils of a first electromagnetic hub bearing 332 and a second electromagnetic hub bearing 336 in opposed axial and radial relationship, respectively with the corresponding coils 326A-C of the first electromagnetic journal bearing and the corresponding coils 328A-C of the second electromagnetic journal bearing.
  • the compressors 268 and 308 of FIGs. 8 and 9 also respectively incorporate integral electric motors 300 and 340 for driving the compressor impeller, eliminating the need for external drive motors and related driving shafts.
  • the compressor 268 incorporates stator coils 302A-C circumferentially embedded about the journal shaft 270 between the recesses 276 and 278, and a corresponding permanent or electromagnetic rotor 304 embedded in a recess within the hub 290.
  • the compressor 308 incorporates stator coils 342A-C circumferentially embedded about the journal shaft 310 between the recesses 320 and 322, and a corresponding permanent or electromagnetic rotor 344 embedded in a recess within the hub 330.
  • the rotor and stator of the respective motors 300 and 340 are configured to generate a magnetic field Fg, for rotating the rotor and its corresponding impeller hub 290, 330.
  • Stator coils 302A-C and 342A-C are selectively energized by a known motor drive and drive control, in order to rotate the respective corresponding hubs 290 and 330.
  • An impeller having a hollow hub, is supported and aligned by interposing a magnetic bearing in the hollow hub, according to methods disclosed herein.
  • the magnetic bearing circumscribes a stationary journal disposed within an impeller cavity of a compressor casing.
  • the stationary journal defines a journal central axis that is congruent with a casing longitudinal axis, with both axes circumscribed by the impeller cavity.
  • At least one electromagnet of the magnetic bearing is energized with a power source; this generates a repulsive magnetic field in the bearing that radially and/or axially positions the journal and hub relative to each other along the journal central axis.
  • the impeller and the stationary journal are selectively aligned relative to each other by varying energization of the electromagnet with the power source.
  • coils of the electromagnet are embedded in the stationary journal.
  • the impeller is driven, rotatively, with a drive shaft coupled thereto, without rotating the stationary journal.
  • the impeller is rotated with an electric motor having stationary stator coils embedded within the stationary journal, which are axially offset from coils of the electromagnet that are also embedded within the stationary journal.
  • rotor coils are embedded within the impeller hub, which are axially offset from coils of the electromagnet that are also embedded within the impeller hub. Coils of the electromagnet are energized, to align the impeller hub and the stationary journal relative to each other.
  • the impeller is driven by energizing the rotor and stator coils.

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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)
  • Magnetic Bearings And Hydrostatic Bearings (AREA)

Abstract

L'invention concerne un compresseur centrifuge (20), avec une roue sans arbre (50), monté de manière rotative sur un tourillon. Le tourillon est intégré dans un arbre de tourillon fixe (40) qui s'étend sur le moyeu de roue (52), ou dans un embout de tourillon (80) qui fait saillie dans au moins l'une des extrémités axiales du moyeu de roue, ou dans une paire de premier et deuxième embouts de tourillon opposés (142, 146). Un palier magnétique (60) est interposé entre le tourillon et un moyeu creux de la roue. Le tourillon et le palier magnétique supportent et positionnent le moyeu de roue dans une cavité de roue du carter de compresseur (22). Un entraînement de roue indépendant (151) fait tourner la roue. Un arbre de transmission (150), qui est indépendant du tourillon, est couplé à la roue. Des aimants permanents de moteur d'entraînement (300), de rotor et de stator respectifs et/ou des bobines électromagnétiques sont intégrés dans le tourillon et le moyeu opposés respectifs.
PCT/US2018/027507 2018-04-13 2018-04-13 Compresseur centrifuge avec roue sans arbre WO2019199321A1 (fr)

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