WO2018054722A1 - Improved arrangement for pressurizing of fluid - Google Patents
Improved arrangement for pressurizing of fluid Download PDFInfo
- Publication number
- WO2018054722A1 WO2018054722A1 PCT/EP2017/072891 EP2017072891W WO2018054722A1 WO 2018054722 A1 WO2018054722 A1 WO 2018054722A1 EP 2017072891 W EP2017072891 W EP 2017072891W WO 2018054722 A1 WO2018054722 A1 WO 2018054722A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- rotor
- compressor
- central shaft
- stage
- pump
- Prior art date
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Classifications
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- 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
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D19/00—Axial-flow pumps
- F04D19/02—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
- F04D19/00—Axial-flow pumps
- F04D19/02—Multi-stage pumps
- F04D19/022—Multi-stage pumps with concentric rows of vanes
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D19/00—Axial-flow pumps
- F04D19/02—Multi-stage pumps
- F04D19/024—Multi-stage pumps with contrarotating parts
-
- 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
Definitions
- the present invention relates to a device for increasing the pressure in a fluid, such as a compressor or pump.
- Compressors or pumps are widely used to increase pressure in a fluid. There is a constant development in the field and there is in general a desire to improve quality and efficiency of compressors and pumps.
- the present invention aims to present a solution for compressors, pumps or the like. In the interface between the rotational and static parts there can be a problem of windage losses or decreased available power for pressure increase.
- the solution aims to reduce windage losses and it's also an object to improve the operating conditions of the proposed solution compared to prior art. Disclosure of the invent ion
- the proposed solution with a modular concept provides the flexibility to adapt to process modifications during the engineering phase and during the pump operation. This is achieved by adjusting the operating speed of the independent modules.
- the m diffusors can be arranged to protrude from the inner perimeter of the shroud and expand in between neighbouring rows of impellers.
- At least two bearings can be arranged between the rotor and the central shaft.
- At least two axial thrust bearings can be arranged axially remote from each other and being associated with the rotor.
- a permanent magnet can be arranged on the rotor in close proximity with the central shaft with magnetic interaction with the motor windings defining a gap dl between the permanent magnet and the motor windings.
- the permanent magnet can be arranged on the inner diameter of the rotor.
- stator and a rotor together forms an electric motor, where the stator can comprise:
- the rotor with an axis of rotation about the central shaft at least comprises:
- each stage at least comprises a central shaft and one rotor where the axis of rotation of each rotor is the associated central shaft and where each rotor at least is provided with a number n>2 rows of impellers arranged at an outer perimeter of its associated rotor with an axial distance between neighbouring rows of impellers.
- At least a first motor winding and first laminations can be arranged in a first central shaft in a first stage li, and a second motor winding and second laminations are arranged in a second central shaft in a second stage h and
- a third motor winding and third laminations are arranged in a third central shaft in a third stage h and
- a fourth motor winding and fourth laminations are arranged in a fourth central shaft in a third stage h.
- all rotors of the compressor or pump stages can rotate in the same direction.
- each of the compressor or pump stages can comprise a motor and an outer shroud surrounding the rotor, where the outer shroud comprises rows of diffusors arranged on the inner diameter of the outer shroud, where the diffusors are arranged to protrude from the inner perimeter of the outer shroud and expand in between neighbouring rows of impellers and where a row of diffusors is arranged between each compressor or pump stage.
- the arrangement can comprise a number of compressor or pump stages arranged radially adjacent with each other
- a first inner stage at least comprises a first inner central shaft and one first inner rotor where the axis of rotation of the first inner rotor is the first inner central shaft
- each rotor at least is provided with a number n>2 rows of impellers arranged at an outer perimeter of its associated rotor with an axial distance between neighbouring rows of impellers.
- At least a first motor winding and first laminations can be arranged in a first central shaft in a first inner stage, and a second outer motor winding and second outer laminations are arranged in the second outer rotor and optionally a third outer motor winding and third outer laminations are arranged in the third outer rotor.
- each compressor or pump stage at least comprises a stator and a rotor which together forms an electric motor, a) where a first inner stator being a part of a first inner motor at least comprises:
- a second outer stator radially outside of a second outer rotor being a part of a second outer motor comprises:
- a permanent second outer magnet arranged on the outer rotor in close proximity with the second outer stator and in magnetic interaction with the second outer motor windings defining a gap dl between the second outer permanent magnet and the second outer motor windings.
- the first inner motor further can comprise two or more bearings arranged between the first inner rotor and the central shaft and at least two first inner axial thrust bearings arranged axially remote from each other and being associated with the first inner rotor and the second outer motor further comprises at least one bearings arranged between the second outer rotor and an annular bearing raceway where the annular bearing raceway is arranged axially adjacent with the first inner stator.
- each of the compressor or pump stages comprises at least, m, rows of diffusors arranged between the second outer stator and the first inner stator.
- the first inner rotors of the compressor or pump stages can rotate in one direction and the second outer rotors of the compressor or pump stages can rotate in an opposite direction.
- the second outer compressor or pump stage comprises a second outer shroud surrounding the second outer stator.
- each stage at least comprises a central shaft and one rotor where the axis of rotation of each rotor (3) is the associated central shaft;
- a first inner stage at least comprises a first inner central shaft and one first inner rotor where the axis of rotation of the first inner rotor is the first inner central shaft
- each rotor at least is provided with one or more rows of impellers with an axial distance between neighbouring rows of impellers.
- a multidimensional scalable compressor and pump system where the compressor or pump stages can be arranged axially adjacent with each other at least comprise a first motor winding and first laminations arranged in a first central shaft in a first stage li, and a second motor winding and second laminations arranged in a second central shaft in a second stage h and optionally a third motor winding and third laminations arranged in a third central shaft in a third stage b.
- the multidimensional scalable compressor and pump system can be arranged axially adjacent with each other at least comprises a stator and a rotor which together forms an electric motor, where the stator at least comprises:
- the rotor with an axis of rotation about the central shaft at least comprises:
- a permanent magnet arranged on the rotor in close proximity with the central shaft and in magnetic interaction with the motor windings defining a gap dl between the permanent magnet and the motor windings.
- a fourth motor winding and fourth laminations can be arranged in a fourth central shaft in a third stage b.
- At least a first motor winding and first laminations can be arranged in a first central shaft in a first inner stage, and a second outer motor winding and second outer laminations are arranged in the second outer rotor and optionally a third outer motor winding and third outer laminations are arranged in the third outer rotor for the compressor or pump stages arranged radially adjacent with each other.
- FIG. 1 shows a cross section of a shaft/ central shaft of a modular pump
- Fig. 2 shows a sectional view showing the basic principles of a modular pump according to one embodiment of the present invention
- Fig. 3 shows a sectional view of a second embodiment of the modular pump according to the present invention
- Fig. 4 shows a sectional view of a third embodiment of the modular pump according to the present invention
- Fig. 5 shows a sectional view of a fourth embodiment of the modular pump according to the present invention
- Fig. 6 shows a fifth embodiment of the modular pump according to the present invention suitable for use in compressors or pumps, and modular pump
- Fig. 7 shows a sixth embodiment of the according to the present invention.
- the arrangement according to the invention is suitable for use in a compressor or pump but can be used in any situation where there is a need to increase pressure in a fluid.
- the invention provides scalability and increased efficiency per volume and simpler arrangement with respect to wiring and bearings. It is an object to provide a ratio between active sections of the motor vs. passive sections optimal, i.e. reduce amount of sections that do not add to efficiency/power relative to sections that increases efficiency/power.
- An optimal ratio between active sections and passive sections for a single pump or compressor module can be achieved by providing two or more rows of impellers per rotor.
- An arrangement with two or more impellers per rotor means that one will have one rotor which provides approximately the same amount of power as two rotors while maintaining the same amount of passive sections, such as motor winding end turn as for traditional "one impeller row per rotor" arrangements where the number of motor end winding would be double.
- Two or more impellers per rotor means that the axial length of the rotor can be shorter than for two rotors having the same characteristics.
- each rotor needs radial and axial bearings, reducing the number of rotors thus implies reducing the number of bearings.
- a basic compressor or pump module comprises at least a central shaft 8 and one rotor 3, where the axis of rotation of the rotor 3 is the central shaft 8.
- the rotor comprises a number, n, of rows of impellers 5 associated with the rotor and with an axial distance between neighbouring rows of impellers 5.
- the central shaft is at least provided with one motor winding 1 and laminations.
- an outboard stator is provided with motor windings and laminations.
- the pump or compressor module can be provided with an outer shroud 12 surrounding the rotor 3, for inboard variants and surrounding an outboard stator for outboard variants.
- the scalability is achieved by providing compressor or pump modules that can be stacked together longitudinally (serially) or radially (in parallel) or in a combination of longitudinally and radially.
- each pump or compressor module will be denoted a stage, either an axial stage or a radial stage.
- a serially stacked configuration provides flexibility with respect to overall power while maintaining a substantially constant diameter. Radial stacking means that it is possible to increase power without adding substantial axial length to a pump or compressor arrangement. Hence, high power vs axial length can be achieved and the power can be increased without adding substantial axial length to a pump or compressor arrangement.
- outer radial stages will be of the outboard type, whilst the inner radial type can be of the inboard type.
- inner radial type can be of the inboard type.
- an electrical motor includes more than one stator then the ratio between active components (stator laminations) and passive components( motor end windings) will provide an increased power per motor length.
- the layout of the pump or compressors according to the present invention combines the possibility of adjusting the speed of the first stages of the rotating equipment to process variations.
- the layout provides the ability to quickly adjust the operating conditions, such as speed or torque as independent rotors and stators can be adjusted in speed and also there is a lower mass moment of inertia of each stage as compared with non-modular conventional solution.
- the first embodiment of the invention relates to single modules of a pump or compressor of the inboard type. With reference to figure 2 it is shown two stages, a first stage and a second stage.
- the first variant of the first embodiment complies with a single stage shown in the figure.
- the first variant of the first embodiment comprises two sets/rows of impellers per rotor.
- the rotor 3 can in principle be described as a disc with two rows of impellers 5 associated with the disc.
- the rotor is adapted to rotate about a central shaft 8.
- the central shaft 8 is in this configuration the stator, i.e. fixed.
- the stator and the rotor 3 together forms an electric motor.
- the stator at least comprises motor windings 1 and laminations.
- Electric wiring 2 which provides for a magnetic field is wound around parts of the laminations in the central shaft 8.
- the wiring 2 shown on each side of the laminations are the same.
- the cooling means can be canals provided in the central shaft 8 for circulation of a cooling fluid.
- the rotor 3 with an axis of rotation about the central shaft 8 is shown with two rows of impellers 5 arranged at an outer perimeter of the rotor, with an axial distance d between the two neighbouring rows of impellers 5.
- a magnet 1 1 is arranged on the rotor 3 in close proximity with the central shaft 8. Hence the magnet 11 is arranged on the inner diameter of the rotor 5.
- the magnet is indicated as a permanent magnet, obviously it is possible to use bars in the motor with an asynchronous typology Hence the rotor can also include laminations.
- the magnet 1 1 is in magnetic interaction with the stator. There is a gap dl between the magnet 1 1 and the stator with its laminations and motor windings 2.
- the compressor or pump stage according to the first variant of the first embodiment comprises two or more radial bearings arranged between the rotor 3 and the central shaft 8 and at least two axial thrust bearings 4 are arranged axially remote from each other and being associated with the rotor 3.
- this configuration with two rows of impellers per rotor implies the same bearing configurations as a rotors with single rows of impellers.
- one row of diffusors 6 can be arranged.
- the diffusor 6 aims to direct a fluid stream so that it hits the impellers in a correct angle.
- the row of diffusors 6 can be fixed to an outer casing or shroud 12 and protrude inwards from this outer shroud 12. There is a gap between the outer diameter of the impellers and the inner diameter of the outer shroud 12. The gap can typically be approximately 1mm so as to minimise fluid "leakage" between impellers 5 and outer shroud 12.
- the first variant of the first embodiment it is shown one row of diffusors in between the rows of impellers, it can also be added rows of diffusors axially to the left and/or right of the impellers i.e. not between.
- the motivation can be to direct fluid in an optimal direction towards the first row of impellers or in the case of added exit diffusors the object can be to direct the direction of flow in an optimal direction with respect to trailing equipment.
- the power density of a stage according to a first variant of the first embodiment is increased as the arrangement is axially more compact than separate pumps or compressors.
- Second variant of first embodiment of the Invention Reference is made to second stage of figure 3, which discloses a single pump or compressor.
- This second variant of the first embodiment is distinguished from the first variant in that it includes three rows of impellers 5 per rotor. This is also an inboard pump or compressor type. Consequently it also includes two rows of diffusors in between the rows of impellers.
- the ratio between active and passive components is even better for this second variant of the first embodiment than it is for the first variant of the first embodiment.
- the power per volume and axial length is increased as compared with the first variant of first embodiment. Note that the same bearing arrangement as for the first variant of the first embodiment is necessary.
- the pump or compressor can be supplied with exit and entrance rows of diffusors.
- the motors are placed in the central axis of the pump or compressor according to the second variant of the first embodiment, it is possible to reduce power loss.
- the first embodiment of the invention can be extended to include any number of impeller rows per rotor, of course restricted by practical/technical limitations.
- the general variant will also include an increased number of diffusors, one row between each row of impellers, hence if n rows of impellers are applied n-1 rows of diffusors can be applied.
- the pump or compressor can be supplied with exit and entrance rows of diffusors.
- the second embodiment of the invention relates to single modules of a pump or compressor of the outboard type. With reference to figure 6 it is shown two stages, a first stage and a second stage.
- the first variant of the second embodiment complies with the first stage shown in figure 6.
- the first variant of the second embodiment comprises two sets/rows of impellers per stator (EMS).
- EMS impellers per stator
- the two rotors can in principle be described as two discs with rows of impellers associated with the disc.
- the rotor is adapted to rotate about a central shaft.
- the central shaft is in this configuration a passive element with diffusors protruding radially outwards from the central shaft.
- one row of diffusors In between the two rows of impellers with an axial distance one row of diffusors is shown.
- the row of diffusors aims to direct a fluid stream so that it hits the impellers at a correct angle.
- one row of diffusors in between the rows of impellers it can also be added rows of diffusors axially to the left and/or right of the impellers i.e. not between.
- the motivation can be to direct fluid in an optimal direction towards the first row of impellers or in the case of added exit diffusors the object can be to direct the direction of flow in an optimal direction with respect to trailing equipment.
- the rotors are provided with magnets, permanent or rotor bars, close to its outer diameter. Outside of the magnets, at an outer diameter of the rotor it is arranged an outer retaining ring which among other shall keep the magnets in place when they are affected by centrifugal forces. There is a gap between the outer diameter of the retaining ring and the inner diameter of an outer - outboard - stator. The gap can typically be approximately 1mm so as to minimise fluid "leakage" between impellers and the outboard stator.
- the stator can comprise motor windings and laminations. Electric wiring which provides for a magnetic field is wound around parts of the laminations of the stator. The wiring is not shown in figure 6. The polarity of the electricity decides whether the stator is North Pole or South Pole. In one embodiment AC-current is used and the polarity of the electro magnet will switch accordingly. Three phase AC-current can be fed to the electric wiring.
- the outboard stator of the pump or compressor according to the first variant of the second embodiment can be provided with cooling means. The cooling means are not shown, however they can be implemented as canals provided in the stator for circulation of a cooling fluid.
- the compressor or pump stage according to the first variant of the second embodiment comprises two or more radial bearings arranged between each rotor and the central shaft and at least two axial thrust bearings are arranged axially remote from each other and being associated with each rotor.
- second stage of figure 6, discloses a single pump or compressor.
- This second variant of the second embodiment is distinguished from the first variant in that it includes three rows of impellers and hence three rotors.
- This is also an outboard pump or compressor type. Consequently it also includes two rows of diffusors in between the rows of impellers protruding out from the central shaft. Additional exit and or entrance diffusors can be added in the same manner as described with reference to the first variant of the second embodiment.
- the ratio between active and passive components is even better for this second variant of the second embodiment than it is for the first variant of the second embodiment, as only one stator is in magnetically interaction with three rows of impellers. Moreover the power per volume and axial length is increased as compared with the first variant of the second embodiment.
- the second embodiment of the invention can be extended to include any number of impeller rows per rotor, of course restricted by practical/technical limitations.
- the general variant will also include an increased number of diffusors, one row of diffusors between each row of impellers, hence if n rows of impellers are applied n-1 rows of diffusors can be applied.
- the pump or compressor can be supplied with exit and entrance rows of diffusors.
- One object of the second embodiment is to drive two or more impellers / rotors by one stator.
- the impellers are not mechanically coupled but just magnetically coupled. By combining more than one stage the power density of the overall system will be increased because of the increased active lamination length with respect to the overall motor length.
- FIG 3 discloses two single pumps or compressors.
- the first stage complies with the first variant of the first embodiment, whilst the second stage complies with the second variant of the first embodiment.
- This second variant of the third embodiment is distinguished from the first variant in that it includes different numbers of rows of impellers between the first and the second stage. This is also an inboard pump or compressor type.
- the third embodiment of the invention can be extended to include more than two pump or compressor stages stacked axially.
- the axially stacked pumps or compressors can be of the first variant first embodiment type, or it can be of the second variant first embodiment type or more generally of the general variant of the first embodiment type. In principle any number of stages can be stacked, only limited by practical and technical reasons.
- the pump or compressor can be supplied with exit and entrance rows of diffusors.
- the first variant of the fourth embodiment of the invention relates to two single modules of a pump or compressor of the outboard type as described above for the first variant of the second embodiment axially stacked together as indicated in figure 6, note that figure 6 second stage shows the second variant of the second embodiment. It is shown two stages, a first stage and a second stage each stage with two rotors. Direction of rotation of the stages can be opposite of each other, i.e. coaxially contra rotating or it can be in the same direction, dependent on the current phase delivered to the electromagnets, EMS of the stators. Dependent on the rotational configuration the diffusors have to be adapted accordingly.
- FIG 6 discloses two single pumps or compressors.
- the first stage complies with the first variant of the second embodiment, whilst the second stage complies with the second variant of the second embodiment.
- This second variant of the fourth embodiment is distinguished from the first variant in that it includes different numbers of rotors between the first and the second stage. This is also an outboard pump or compressor type.
- the fourth embodiment of the invention can be extended to include more than two pump or compressor stages stacked axially.
- the axially stacked pumps or compressors can be of the first variant second embodiment type, or it can be of the second variant second embodiment type or more generally of the general variant of the second embodiment type.
- any number of stages can be stacked, only limited by practical and technical reasons.
- direction of exit stream of fluid from one stage must be adapted to the entrance of a trailing stage.
- the pump or compressor can be supplied with exit and entrance rows of diffusors.
- Figure 4 shows a multistage inboard outboard configuration.
- the inboard stages includes two stages axially arranged. In between the two axially arranged inboard stages it is provided an annular bearing raceway.
- the annular bearing raceway in the figure represents a portion of the central shaft with an enlarged diameter.
- the size of the inner diameter of the inner perimeter of a rotor adapted to rotate around a central shaft on said bearing raceway dictates the outer diameter of the annular bearing raceway.
- a second bearing raceway associated with a second rotor associated with a second radial stage second axial stage can be provided on the central shaft. Bearings are provided between stator and rotor, i.e.
- the compressor or pump stage according to the fifth embodiment comprises at least one radial bearings arranged between rotor and the central shaft or the annular bearing raceway and at least two axial thrust bearings arranged axially remote from each other and being associated with the same rotor. It shall be noted that configurations with two or more rows of impellers per rotor implies the same bearing configurations as a rotors with single rows of impellers.
- the axis of rotation is the central longitudinal axis of the central shaft.
- the multistage inboard outboard configuration can be seen as four stages of pumps or compressors, a first axial inboard stage to the left in the figure and a second axial inboard stage to the right in the figure, both being the stages radially closest to the central shaft.
- Each stage includes elements as indicated in the first embodiments above.
- the rotors of the inboard stages are provided with magnets, permanent or rotor bars, close to its inner diameter. There is a gap between the inner diameter of the magnets and the outer diameter of the central. The gap can typically be approximately 1mm so as to minimise fluid "leakage” between impellers and the outboard stator.
- the inboard outboard multistage configuration comprises a first axial stage second radial outboard stage being the pump or compressor stage radially next to the first axial inboard stage.
- the first axial stage second radial outboard stage comprises a rotor with the central shaft as an axis of rotation.
- the rotor of the first axial stage second radial outboard stage is provided with bearings between the annular bearing raceway and said rotor.
- the rotors of the outboard stages are provided with magnets, permanent or rotor bars, close to its outer diameter. Outside of the magnets, at an outer diameter of the rotor it can be arranged an outer retaining ring which among other shall keep the magnets in place when they are affected by centrifugal forces. There is a gap between the outer diameter of the retaining ring and the inner diameter of an outer - outboard - stator. The gap can typically be approximately 1mm so as to minimise fluid "leakage" between impellers and the outboard stator.
- the rotor of the first axial stage second radial outboard stage rotates according to figure 4 in the opposite direction of the first inboard and second inboard axial rotors.
- a second axial stage second radial outboard stage substantially equal to the first axial stage second radial outboard stage is arranged axially adjacent the first axial stage second radial outboard stage.
- the configuration with four stages, a first axial inboard stage, a second axial inboard stage, a first axial second radial outboard stage and a second axial stage second radial outboard stage according to figure 4 shows that axially neighbouring impellers rotates in the same direction whilst inboard and outboard stages next to each other rotates in the opposite directions. Diffusors are arranged in between impellers.
- the diffusor - rotor configuration is as follows: diffusor rotor first axial inboard stage ⁇ diffusor rotor first axial second radial outboard stage ⁇ diffusor rotor second axial inboard stage diffusor rotor second axial second radial outboard stage.
- Figure 4 shows the rotors without any indication of the number of rows of impellers per rotor. Each rotor can hold more than one row of impellers in the same manner as described with reference to previous embodiments.
- the multistage inboard outboard configuration of figure 4 according to the fifth embodiment can be repeated serially so that a second and/or third multistage inboard outboard stage can be arranged axially to the left or right.
- the first and second axial stage in figure 4 is provided with cooling means.
- the cooling means can be canals provided in the central shaft for circulation of a cooling fluid.
- these cooling means can be provided as canals.
- the direction of rotation for the rotors according to the fifth embodiment can be configured differently from what is indicated in figure 4.
- the central shaft is fixed and the direction of rotation is dictated by the direction of the magnetic fields the rotors can be configured to rotate in any direction without creating torque problems.
- direction of rotation affects fluid streams and the design of the diffusors and rotor blades.
- FIG 5 shows a hybrid solution with a first inner stage, where the first inner stage comprises a central shaft with motor windings.
- a first rotor with a permanent magnet rotates about the central shaft, with the central axis of the central shaft as an axis of rotation.
- Two rows, Rl and R2 of impellers are fixed to the rotor.
- a second outer radial stage includes a second radially outer rotor rotating in an opposite direction of the first rotor.
- the second radially outer rotor includes two impellers, SI and S2, which is arranged in between the impellers of the inner stage. Outside of the second rotor it is arranged a second outboard stator with motor windings.
- a pump or compressor includes two outboard stators adjacent each other provided with motor windings.
- Rotors are provided radially oriented between the outboard stators and a central shaft.
- the rotors can include an inner hollow axle, i.e. a pipe, which can rotate about the central shaft.
- On the inner hollow axle it is provided two or more axially separated impellers.
- the rotor arrangement can be seen as the hollow axle with a number of disc-shaped rotors attached thereto. The number of axially oriented rotors fixed to the same hollow axle is a matter of design.
- a retaining ring can be provided to keep the magnets on place when influenced by centrifugal forces.
- the magnets of the rotors magnetically interacts with one or more outboard stator.
- Diffusors are arranged between the impellers.
- the impellers can be fixed to the outboard stators.
- the diffusors protrudes inwards from the stators.
- a single stage comprises one hollow axle adapted to rotate around a central fixed shaft, associated with at least two rotors and the necessary stators as indicated in figure 7 where a two rotor configuration is shown.
- a pump or compressor comprises at least one stage.
- a stage comprises at least a stator and a rotor with associated elements.
- inboard stages and outboard stages Stages can be combined axially and or radially.
- a two stage module as shown in figure 2 can be extended into several axially oriented inboard modules. The same applies to the module shown in figure 3.
- Figure 4 is a 4 stage module which can be combined with similar four stage modules.
- Figure 5 is a hybrid module, the module scales axially well, i.e. can be combined axially with similar modules.
- the module of figure 6 shows two outboard stages, a plurality of such stages/modules can be axially/serially combined, the same applies to the module in figure 7.
- the ratio between rows of impellers vs. number of rotors per stage between modules does not necessarily be the same for the configurations described with reference to figure 2 - 7.
- inboard and outboard motors enables to increase the axial length of the active part (laminations) for each electric motor and increase the overall power density.
Abstract
Description
Claims
Priority Applications (5)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
GB1905326.3A GB2569916B (en) | 2016-09-20 | 2017-09-12 | Improved arrangement for pressurizing of fluid |
AU2017331312A AU2017331312B2 (en) | 2016-09-20 | 2017-09-12 | Improved arrangement for pressurizing of fluid |
BR112019005406A BR112019005406A2 (en) | 2016-09-20 | 2017-09-12 | improved arrangement for pressurizing fluid |
US16/334,933 US11639723B2 (en) | 2016-09-20 | 2017-09-12 | Arrangement for pressurizing of fluid |
US18/125,637 US20230235740A1 (en) | 2016-09-20 | 2023-03-23 | Arrangement for pressurizing of fluid |
Applications Claiming Priority (4)
Application Number | Priority Date | Filing Date | Title |
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NO20161502 | 2016-09-20 | ||
NO20161502 | 2016-09-20 | ||
NO20171365 | 2017-08-17 | ||
NO20171365A NO20171365A1 (en) | 2016-09-20 | 2017-08-17 | Improved arrangement for pressurizing of fluid |
Related Child Applications (2)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US16/334,933 A-371-Of-International US11639723B2 (en) | 2016-09-20 | 2017-09-12 | Arrangement for pressurizing of fluid |
US18/125,637 Division US20230235740A1 (en) | 2016-09-20 | 2023-03-23 | Arrangement for pressurizing of fluid |
Publications (1)
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WO2018054722A1 true WO2018054722A1 (en) | 2018-03-29 |
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PCT/EP2017/072891 WO2018054722A1 (en) | 2016-09-20 | 2017-09-12 | Improved arrangement for pressurizing of fluid |
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Citations (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US2384000A (en) * | 1944-05-04 | 1945-09-04 | Frank L Wattendorf | Axial flow fan and compressor |
US2451944A (en) * | 1942-01-21 | 1948-10-19 | Vickers Electrical Co Ltd | Axial flow compressor and like machines |
US2461931A (en) * | 1943-01-04 | 1949-02-15 | Vickers Electrical Co Ltd | Multistage compressor |
RU2458253C1 (en) * | 2011-03-18 | 2012-08-10 | Закрытое акционерное общество "Научно-исследовательский и конструкторский институт центробежных и роторных компрессоров им. В.Б. Шнеппа" | Radial-flow compressor unit |
EP2824330A1 (en) * | 2013-07-12 | 2015-01-14 | Johnson Controls Denmark ApS | An axial compressor and use of an axial compressor |
WO2015114136A1 (en) * | 2014-02-03 | 2015-08-06 | Nuovo Pignone Srl | Multistage turbomachine with embedded electric motors |
-
2017
- 2017-09-12 WO PCT/EP2017/072891 patent/WO2018054722A1/en active Application Filing
Patent Citations (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US2451944A (en) * | 1942-01-21 | 1948-10-19 | Vickers Electrical Co Ltd | Axial flow compressor and like machines |
US2461931A (en) * | 1943-01-04 | 1949-02-15 | Vickers Electrical Co Ltd | Multistage compressor |
US2384000A (en) * | 1944-05-04 | 1945-09-04 | Frank L Wattendorf | Axial flow fan and compressor |
RU2458253C1 (en) * | 2011-03-18 | 2012-08-10 | Закрытое акционерное общество "Научно-исследовательский и конструкторский институт центробежных и роторных компрессоров им. В.Б. Шнеппа" | Radial-flow compressor unit |
EP2824330A1 (en) * | 2013-07-12 | 2015-01-14 | Johnson Controls Denmark ApS | An axial compressor and use of an axial compressor |
WO2015114136A1 (en) * | 2014-02-03 | 2015-08-06 | Nuovo Pignone Srl | Multistage turbomachine with embedded electric motors |
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