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WO2017015729A1 - Compresseur centrifuge électrique muni de canaux dans le moyeu de roue pour purger l'air et refroidir le moteur et les paliers - Google Patents

Compresseur centrifuge électrique muni de canaux dans le moyeu de roue pour purger l'air et refroidir le moteur et les paliers Download PDF

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Publication number
WO2017015729A1
WO2017015729A1 PCT/BE2016/000034 BE2016000034W WO2017015729A1 WO 2017015729 A1 WO2017015729 A1 WO 2017015729A1 BE 2016000034 W BE2016000034 W BE 2016000034W WO 2017015729 A1 WO2017015729 A1 WO 2017015729A1
Authority
WO
WIPO (PCT)
Prior art keywords
channels
impeller
centrifugal
cooling
bearings
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.)
Ceased
Application number
PCT/BE2016/000034
Other languages
English (en)
Inventor
Erik Paul Fabry
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.)
Atlas Copco Airpower NV
Original Assignee
Atlas Copco Airpower NV
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 Atlas Copco Airpower NV filed Critical Atlas Copco Airpower NV
Publication of WO2017015729A1 publication Critical patent/WO2017015729A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

Links

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
    • F04D29/26—Rotors specially for elastic fluids
    • F04D29/28—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps
    • F04D29/284—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps for 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
    • 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
    • F04D29/02—Selection of particular materials
    • F04D29/023—Selection of particular materials especially adapted for elastic fluid 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
    • F04D29/00—Details, component parts, or accessories
    • F04D29/58—Cooling; Heating; Diminishing heat transfer
    • F04D29/5806—Cooling the drive system
    • 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
    • F04D29/584—Cooling; Heating; Diminishing heat transfer specially adapted for elastic fluid pumps cooling or heating the machine
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
    • F05D2230/00—Manufacture
    • F05D2230/20—Manufacture essentially without removing material
    • F05D2230/22—Manufacture essentially without removing material by sintering
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
    • F05D2230/00—Manufacture
    • F05D2230/30—Manufacture with deposition of material
    • F05D2230/31—Layer deposition

Definitions

  • the present invention relates to a centrifugal impeller and a centrifugal machine equipped with such an impeller.
  • the invention is intended for centrifugal machines such as a turbocompressor, turbine or similar .
  • a centrifugal compressor element as used in turbocompressors consists of an impeller that is rotatably affixed in a housing with an axial inlet and a radial outlet, whereby the impeller is formed by a type of trumpet-shaped hub to bend the gas drawn in from the axial direction at the inlet to the radial direction at the outlet, and by blades that are provided on the hub and which together with the hub and the housing define channels through which the gas is guided to compress it.
  • the impeller can be provided with a central borehole to be able to fasten the impeller at one end of a drive shaft, whereby this drive shaft is driven by a motor.
  • the central borehole does not necessarily have to be present .
  • Such an impeller can also be a closed impeller that is provided with a Shroud' , but this is not necessarily the case .
  • the motor that is used to drive the impeller will generate heat and heat will also be generated during compression.
  • the motor is a high speed motor for driving the impeller at high speeds of rotation. Consequently this motor has a high energy density and cooling is of great importance.
  • Backup bearings are roller bearings by which the impeller is mounted on bearings in the housing and will only be used when the magnetic bearings, by which the impeller is mounted on bearings in the housing in normal conditions, are not active, for example due to a power failure, to enable the impeller to come to a stop with these backup bearings .
  • a disadvantage is that extra means always have to be provided for the cooling of the motor, impeller and bearings .
  • these extra means consist of an extra fan, extra filters and similar.
  • cooling fans are placed on the housing, these extra means consist of an extra fan with motor, extra filters, electrical and other connections, control units, control logic and similar.
  • the purpose of the present invention is to provide a solution to a least one of the aforementioned and other disadvantages .
  • the object of the present invention is a centrifugal impeller with a hub with a hub surface and a central shaft, whereby this hub increases in diameter in the direction from an inlet side to an outlet side of the impeller, whereby the hub is provided with a back wall on the outlet side, whereby the impeller comprises a number of protruding blades that are provided on the hub surface, whereby the hub is provided with channels that extend from an input opening in the hub surface to an output opening in the back wall, whereby these channels split off a proportion of the gas that is drawn in and guide it to the back wall of the impeller.
  • An advantage is that a proportion of the gas drawn in can be split off via the channels and can be used as cooling gas to cool the motor and any other components of the centrifugal machine in which the centrifugal impeller is used.
  • Another advantage is that even if there is a power failure, there will still be cooling while the impeller comes to a stop, so that the backup bearings, the motor and the impeller are still cooled.
  • the hub is at least partially hollow with one or more hollow spaces, whereby the aforementioned channels are formed by one or more of the aforementioned hollow spaces or whereby at least a portion of the channels at least partially coincide or overlap to form a hollow space.
  • An at least partially hollow hub does not exclude certain structures being provided in the one or more hollow spaces of the hub, such as for example reinforcing ribs and similar .
  • An advantage of this is that the mass of the impeller is reduced so that higher speeds of the impeller are possible, which is useful for an energy-efficient operation of the centrifugal machine in which the impeller is used.
  • the bearings of the central shaft are also loaded less, such that for the design of a centrifugal machine smaller bearings can be selected resulting in a lower cost price and/or a more compact compressor element or a central shaft with a smaller diameter.
  • the impeller is produced by means of an additive production method.
  • Additive production refers to a category of production methods, for example powder bed fusion whereby thermal energy is utilised to selectively enable certain regions in a powder bed to fuse together, or by direct energy deposition whereby beamed thermal energy is used to make materials melt while they are deposited.
  • the category of powder bed fusion there are a number of technologies such as electron beam melting, whereby powder material is melted by using an electron beam; selective laser melting whereby powder material is melted by means of a laser; selective laser sintering whereby powder material is sintered by using a laser.
  • the category of direct energy deposition includes the technology of laser cladding.
  • a centrifugal machine means a turbocompressor or turbine for example, but the invention is not limited to this.
  • the present invention also concerns a method for cooling a centrifugal machine, whereby use is made of a centrifugal machine according to the invention, whereby a proportion of the gas drawn in is split off via the channels in the centrifugal impeller and guided to the back wall of the impeller so that the split-off gas can be used for cooling the centrifugal machine.
  • the advantages of such a centrifugal machine and method according to the invention are analogous to the advantages of a centrifugal impeller according to the invention cited above .
  • FIG. 1 schematically shows a centrifugal machine with one single centrifugal impeller according to the invention
  • figure 2 schematically shows a perspective view of a centrifugal impeller according to the invention with a partial cutaway;
  • figure 3 shows an alternative embodiment of the section that is shown in figure 2 by F3;
  • figure 4 shows an alternative embodiment of figure 3
  • figure 5 shows two possible cross-sections according to the line V-V in figure 3;
  • FIG 6 shows a variant of a machine with two centrifugal impellers according to the invention.
  • the centrifugal machine 1 shown in figure 1 is centrifugal compressor element with a housing 2 in which drive shaft 3 is mounted on bearings .
  • the aforementioned bearings 4 can also comprise a pair backup bearings .
  • a centrifugal impeller 5 according to the invention affixed on the drive shaft 3.
  • a motor 6 is provided to drive the drive shaft 3.
  • An inlet 7 is provided in the housing 2 for the supply of gas to be compressed and an outlet 8 for the outflow of compressed gas.
  • the inlet side 9 of the impeller 5 is located at the aforementioned inlet 7 and the outlet side 10 is located at the aforementioned outlet 8.
  • Figure 2 shows the centrifugal impeller 5 in more detail.
  • the impeller 5 comprises a hub 11 with a hub surface 12 and a central shaft 13 with a borehole 14 that is intended to be coupled to the drive shaft 3.
  • the hub 11 increases in diameter in the direction from the inlet side 9 to the outlet side 10 of the impeller 5 so that the hub 11 takes on a type of trumpet shape, whereby the hub surface 12 goes slantwise from an essentially axial direction X-X' on the inlet side 9 to an essentially radial direction Y-Y' on the outlet side 10.
  • the hub 11 is provided with a back wall 15 on the outlet side 10.
  • a seal 16 is provided on the back wall that will ensure that the hot compressed air remains separated from the motor compartment.
  • a number of protruding blades 17 are provided on the hub surface 12.
  • two series of blades 17 are provided, i.e. on the one hand main blades 17a that extend over a certain length from the axially oriented inlet side 9 of the hub 5 to the radially oriented outlet side 10 of the hub 5, and ⁇ splitter blades' 17b on the other hand that extend over a shorter length between the main blades 17a, starting at an axial distance from the inlet side 9 of the hub 5 up to the outlet side 10 of the hub 5.
  • the invention is not limited to two series of blades 17, but is also applicable to any number of series of blades 17, whereby for example there are no splitter blades 17b or on the contrary a number of series of splitter blades 17b can be provided.
  • the hub 5 is provided with one or more channels 18 that extend through the hub 5.
  • the channels 18 extend from an input opening 19 that is located in the hub surface 12 up to an output opening 20 in the back wall 15.
  • the channels 18 will be able to split off a proportion of the gas that is drawn in so that this split-off gas is guided via the input openings 19 and the channel 18 to the output opening 20 and the back wall 15 of the impeller 5.
  • the input opening 19 in the hub surface 12 is at an axial distance A from the inlet side 9, at a radial distance B from the shaft 13. It is not excluded that this last distance B is almost zero, in other words that the input opening 19 is at the location of the inlet side 9.
  • the output opening 20 is in the back wall 15 at a radial distance C that is greater than the aforementioned distance B.
  • the channels 18 will bend in the direction from the input opening 19 to the output opening 20 in the radial direction Y-Y' , away from the central shaft 13.
  • the channels 18 have an essentially square or rectangular cross-section. However, it is not excluded that the channels 18 have a round or oval cross-section.
  • the cross-section of the channels 18 varies in the direction from the input opening 19 to the output opening 20.
  • the variation of the cross-section of the channels 18 will ensure that the flow or circulation in the channel 18 is optimum.
  • the number and form of the channels 18 and the input openings 19 is such that around 10 percent to 35 percent, for example 25 percent, of the gas drawn in by the centrifugal compressor element 1 can be split off and transported via the input openings 19, the channels 18 and the output opening 20.
  • the operation of the centrifugal compressor element 1 is very simple and as follows.
  • the motor 6 will drive the drive shaft 3 such that the centrifugal impeller 5 will rotate.
  • a portion of the air drawn in, in this case 25 percent, will be split off via the channels 18 and transported to the back wall 15 of the impeller 5.
  • the split-off air can flow through optimally and be transported to the drive shaft 3 and the motor 6 for the cooling thereof.
  • the split-off air can also cool the impeller 5.
  • the channels 18 to the back wall 15 of the impeller 5 for cooling air thus form an internal fan as it were that is integrated in the impeller 5.
  • the cooling air that is blown out by this internal fan along the back wall 15 can be used to cool different components, more specifically the various bearings 4 and the electric motor 6.
  • the cooling air that leaves the impeller 5 can flow freely to the components that are behind the impeller 5 or can be received by fixed cooling channels 21 that guide the cooling air to the specific components and which are schematically shown in figure 1.
  • These fixed cooling channels 21 can be processed in the housing of the centrifugal machine 1, which in the case of the example of figure 1 is composed of the housing 2 of the compressor element and the stator 6b of the motor.
  • These internal fixed channels 21 can be realised for example by means of 3D printing, casting or by machining techniques, or can be formed by external pipes or channels, or can be formed by assembling different components that form an enclosed space such as the space 22 between the rotor 6a and the stator 6b of the motor 6.
  • stator blades At the inlet of a fixed cooling channel 21 it is possible to provide stator blades, not shown, to reduce the air speeds and build up the pressure to provide the components with cooling air with lower flow losses.
  • a fixed cooling channel 21 At the inlet of a fixed cooling channel 21 it is also possible to provide adjustable stator blades or an adjustable restriction to control the quantity of cooling air, for example as a function of the motor load.
  • control of the decrease of the quantity of cooling air is an indirect control of the quantity of air that the impeller will compress. It is thus a capacity control of the centrifugal machine 1 as a centrifugal compressor 1 for example, without other parameters such as speed or similar changing in the centrifugal machine 1.
  • this indirect capacity control for operation at low capacity, i.e. if too much cooling air is tapped off from the impeller 5, a channel 23 or opening will let the surplus quantity of cooling air escape to the environment via a controllable bypass valve 24.
  • Such a capacity control can, alone or together with other controls, guarantee that the centrifugal machine is kept outside the unstable "surge” region (or “pumping") of the centrifugal compressor, for example together with, and without any restriction, a speed control, variable inlet blades, variable outlet blades, etc.
  • bearings 4 on either side of the electric motor, when viewed in the axial direction, that can consist of radial bearings only or radial and axial bearings.
  • the various components remain below an imposed maximum permissible temperature.
  • the motor windings do not exceed a certain temperature in order to prevent degradation of the lacquer on the motor windings .
  • the cooling air is divided into separate channels 21 behind the impeller 5 for the first set of bearings 4, the second set of bearings 4 and the electric motor 6.
  • the supply of cooling air originating from the internal channels 18 is preferably directly in the bearing 4.
  • the advantage of this invention is that large quantities of air at low temperature are introduced compared to a supply of a small amount of leakage air at a higher temperature from the outside diameter of the impeller 5.
  • the use of the leakage air from the outside diameter of the impeller 5 is not energy efficient as a lot of energy has already been consumed to bring this air to the higher pressure at the outside diameter of the impeller 5.
  • roller bearings or ball bearings as used for the backup bearings, with rollers or balls between an inner race and an outer race, direct cooling by oil-free air such as in the bottom half of figure 1 is not recommended, as such bearings 4 are grease-lubricated or oil-lubricated and cooled oil-free air can dry out these lubricants.
  • the roller bearings or ball bearings it is consequently appropriate for the roller bearings or ball bearings to be cooled by a portion of cooling channels 21 that are in the housing around the outer race of the bearings 4, as in the top half of figure 1.
  • FIG. 3 shows an alternative embodiment of an impeller 5 according to the invention.
  • the hub 11 is hollow with a number of hollow spaces 26.
  • the hub 11 is hollow, the hub 11 will have a lower weight with the aforementioned accompanying advantages. At least a portion of the aforementioned channels 18 at least partially border one another in the peripheral direction. It is also possible that alternatively at least a portion of the channels 18 at least partially coincide or overlap.
  • the channels 18 that border one another in the peripheral direction are separated from one another by ribs 27 that extend radially or as good as radially.
  • the ribs 27 act as a separating wall between the various channels 18.
  • the channels 18 can be made larger, without jeopardising the sturdiness of the hub 11.
  • the rib 27 is constructed as a fan blade. Such ribs 27 will have a type of compressor action.
  • the top drawing shows the shape of the cross- section of such a rib 27.
  • the ribs 27 will have the effect that during the operation of the centrifugal impeller 5, the split-off air is compressed so that a good circulation of the split-off cooling air can be obtained.
  • Figure 4 shows an alternative embodiment of figure 3.
  • the channels 18 do not bend, or hardly bend, in the radial direction Y-Y' .
  • the distance B is approximately equal to the distance C.
  • the cross-section of the channel 18 does not vary either or barely varies .
  • the distance C is less than the distance B. This means that the channels 18 bend in the radial direction Y-Y' towards the shaft 13. In this last case the split-off air will expand due to the turbine action of the channels 18.
  • the ribs 27 are constructed as turbine blades.
  • Such an application is used for example in the second stage of a two-stage compressor, whereby the air in the inlet 8 is already at a higher pressure and will be expanded by the turbine blades in the channels 18 to ambient pressure or approximately ambient pressure before being guided to the motor 6, the drive shaft 3 and the backup bearings for the cooling thereof.
  • An advantage of this is that the split-off gas that was compressed will be cooled by the expansion, so that it will be able to cool optimally.
  • An additional advantage is that the energy released during the expansion can be recuperated.
  • the ribs 27 and/or blades 17 that form the channels 18 are continuously connected to the blades 17 of the impeller 5, this is in contrast to what is described in DE 10.2007.021.934 in which there is a case of a first and a second set of blades that are missing in the case of the invention. Due to the design in the peripheral direction, as illustrated in figure 5, and the axial direction, as shown in figures 3 and 4, it is possible to obtain a fan operation with a pressure increase and to obtain a turbine operation with an expansion with a pressure decrease.
  • the aforementioned ribs 27 are formed by a radial extension of the blades 17 of the impeller 5 towards the central shaft 13 up to the channels 18 or the hollow spaces 26.
  • the form, curvature, etc, of the ribs 27 in the channels 18 will differ from the form, curvature, etc, of the actual blades 17. It is not excluded that only a portion of the ribs 27 are formed by a radial extension of the blades 17 and that this is not the case for a different portion of the ribs 27.
  • similar ribs 27 are provided in the channels 18 that extend radially or approximately radially to strengthen the hub 11 of the impeller 5. Note that in this case the ribs 27 do not act as a separating wall between the different channels 18.
  • impellers 5 In the case of a centrifugal compressor such as in figure 6 with impellers 5 on either side of the electric motor 6, it is possible that one or both impellers 5 have a higher inlet pressure than the ambient pressure.
  • the pressure in the space 22 of the electric motor 6 is preferably close to ambient pressure (lowest pressure) so that the eddy losses due to air friction losses are a minimum. If one impeller draws in from the environment, the cooling air is preferably provided via this impeller 5.
  • the present invention is by no means limited to the embodiments described as an example shown in the drawings, but a centrifugal impeller according to the invention, a centrifugal machine according to the invention and a method for cooling a centrifugal machine can be realised in all kinds of variants without departing from the scope of the invention .

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

Abstract

L'invention concerne une roue centrifuge comprenant un moyeu (11) présentant une surface de moyeu (12) et un arbre central (13), le diamètre du moyeu (11) augmentant dans la direction allant d'un côté entrée (9) à un côté sortie (10) de la roue (5), ledit moyeu (11) étant doté d'une paroi arrière (15) sur le côté sortie (10), la roue (5) comprenant un certain nombre d'aubes faisant saillie (17) qui sont disposées sur la surface de moyeu (12), caractérisée en ce que le moyeu (11) est doté de canaux (18) qui s'étendent à partir d'une ouverture d'entrée (19) dans la surface de moyeu (12) vers une ouverture de sortie (20) dans la paroi arrière (15), ces canaux (18) divisant une partie du gaz qui est aspiré à l'intérieur et guidant celui-ci vers la paroi arrière (15) de la roue (5).
PCT/BE2016/000034 2015-07-29 2016-07-27 Compresseur centrifuge électrique muni de canaux dans le moyeu de roue pour purger l'air et refroidir le moteur et les paliers Ceased WO2017015729A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
BE2015/5485 2015-07-29
BE2015/5485A BE1023309B1 (nl) 2015-07-29 2015-07-29 Centrifugaal schoepenrad, centrifugale machine uitgerust met dergelijk schoepenrad en werkwijze voor het koelen van een centrifugale machine

Publications (1)

Publication Number Publication Date
WO2017015729A1 true WO2017015729A1 (fr) 2017-02-02

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PCT/BE2016/000034 Ceased WO2017015729A1 (fr) 2015-07-29 2016-07-27 Compresseur centrifuge électrique muni de canaux dans le moyeu de roue pour purger l'air et refroidir le moteur et les paliers

Country Status (2)

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BE (1) BE1023309B1 (fr)
WO (1) WO2017015729A1 (fr)

Cited By (11)

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CN108869037A (zh) * 2018-09-14 2018-11-23 青岛云深动力科技有限公司 燃气轮机
CN110145479A (zh) * 2019-05-23 2019-08-20 大连海事大学 一种自带电机转子冷却系统的电动空压机
EP3569869A4 (fr) * 2017-02-23 2020-01-15 Mitsubishi Heavy Industries Compressor Corporation Machine rotative
EP3771834A1 (fr) * 2019-08-02 2021-02-03 Hamilton Sundstrand Corporation Trajets de refroidissement de moteur et de palier
CN113404705A (zh) * 2021-06-28 2021-09-17 鑫磊压缩机股份有限公司 一种带过滤系统的空气悬浮鼓风机
CN113669273A (zh) * 2021-08-11 2021-11-19 鑫磊压缩机股份有限公司 一种磁悬浮离心机鼓风机
WO2022122786A1 (fr) * 2020-12-11 2022-06-16 Robert Bosch Gmbh Turbomachine, en particulier pour un système de pile à combustible
CN114962302A (zh) * 2022-06-17 2022-08-30 浙江科力风机有限公司 节能环保型离心风机
CN116538110A (zh) * 2023-06-20 2023-08-04 山东华东风机有限公司 一种磁悬浮空气压缩机
WO2025215239A1 (fr) * 2024-04-12 2025-10-16 Thermodyn Ensemble moteur-compresseur intégré
FR3161265A1 (fr) * 2024-04-12 2025-10-17 Thermodyn Ensemble moteur-compresseur intégré

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US2494200A (en) * 1946-02-12 1950-01-10 Ramqvist Nils Allan Electric machine
US2620123A (en) * 1946-05-31 1952-12-02 Continental Aviat & Engineerin Cooling system for combustion gas turbines
US5108261A (en) * 1991-07-11 1992-04-28 United Technologies Corporation Compressor disk assembly
US20060204371A1 (en) * 2005-03-14 2006-09-14 Kaeser Kompressoren Gmbh Compressor assembly having an air-cooled electric motor
DE102007021934A1 (de) 2007-05-10 2008-11-20 Daimler Ag Ladervorrichtung für eine Brennkraftmaschine sowie Brennkraftmaschine
WO2013124314A1 (fr) * 2012-02-23 2013-08-29 Nuovo Pignone Srl Fabrication d'hélice de turbine

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2494200A (en) * 1946-02-12 1950-01-10 Ramqvist Nils Allan Electric machine
US2620123A (en) * 1946-05-31 1952-12-02 Continental Aviat & Engineerin Cooling system for combustion gas turbines
US5108261A (en) * 1991-07-11 1992-04-28 United Technologies Corporation Compressor disk assembly
US20060204371A1 (en) * 2005-03-14 2006-09-14 Kaeser Kompressoren Gmbh Compressor assembly having an air-cooled electric motor
DE102007021934A1 (de) 2007-05-10 2008-11-20 Daimler Ag Ladervorrichtung für eine Brennkraftmaschine sowie Brennkraftmaschine
WO2013124314A1 (fr) * 2012-02-23 2013-08-29 Nuovo Pignone Srl Fabrication d'hélice de turbine

Cited By (15)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3569869A4 (fr) * 2017-02-23 2020-01-15 Mitsubishi Heavy Industries Compressor Corporation Machine rotative
US10808723B2 (en) 2017-02-23 2020-10-20 Mitsubishi Heavy Industries Compressor Corporation Rotary machine
CN108869037A (zh) * 2018-09-14 2018-11-23 青岛云深动力科技有限公司 燃气轮机
CN110145479A (zh) * 2019-05-23 2019-08-20 大连海事大学 一种自带电机转子冷却系统的电动空压机
US11143203B2 (en) 2019-08-02 2021-10-12 Hamilton Sundstrand Corporation Motor and bearing cooling paths
EP3771834A1 (fr) * 2019-08-02 2021-02-03 Hamilton Sundstrand Corporation Trajets de refroidissement de moteur et de palier
WO2022122786A1 (fr) * 2020-12-11 2022-06-16 Robert Bosch Gmbh Turbomachine, en particulier pour un système de pile à combustible
CN113404705A (zh) * 2021-06-28 2021-09-17 鑫磊压缩机股份有限公司 一种带过滤系统的空气悬浮鼓风机
CN113669273A (zh) * 2021-08-11 2021-11-19 鑫磊压缩机股份有限公司 一种磁悬浮离心机鼓风机
CN114962302A (zh) * 2022-06-17 2022-08-30 浙江科力风机有限公司 节能环保型离心风机
CN114962302B (zh) * 2022-06-17 2023-09-26 浙江科力风机有限公司 节能环保型离心风机
CN116538110A (zh) * 2023-06-20 2023-08-04 山东华东风机有限公司 一种磁悬浮空气压缩机
CN116538110B (zh) * 2023-06-20 2024-02-13 山东华东风机有限公司 一种磁悬浮空气压缩机
WO2025215239A1 (fr) * 2024-04-12 2025-10-16 Thermodyn Ensemble moteur-compresseur intégré
FR3161265A1 (fr) * 2024-04-12 2025-10-17 Thermodyn Ensemble moteur-compresseur intégré

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