WO2023083588A1 - Compresseur radial et procédé de fonctionnement d'un compresseur radial - Google Patents

Compresseur radial et procédé de fonctionnement d'un compresseur radial Download PDF

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Publication number
WO2023083588A1
WO2023083588A1 PCT/EP2022/079508 EP2022079508W WO2023083588A1 WO 2023083588 A1 WO2023083588 A1 WO 2023083588A1 EP 2022079508 W EP2022079508 W EP 2022079508W WO 2023083588 A1 WO2023083588 A1 WO 2023083588A1
Authority
WO
WIPO (PCT)
Prior art keywords
impeller
wheel
flow resistance
centrifugal compressor
compressor
Prior art date
Application number
PCT/EP2022/079508
Other languages
German (de)
English (en)
Inventor
Tobias Reinhard OTT
Original Assignee
Robert Bosch Gmbh
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 Robert Bosch Gmbh filed Critical Robert Bosch Gmbh
Publication of WO2023083588A1 publication Critical patent/WO2023083588A1/fr

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
    • F04D29/00—Details, component parts, or accessories
    • F04D29/05—Shafts or bearings, or assemblies thereof, specially adapted for elastic fluid pumps
    • F04D29/051—Axial thrust balancing
    • 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
    • F04D29/08—Sealings
    • F04D29/10—Shaft sealings
    • F04D29/12—Shaft sealings using sealing-rings
    • F04D29/122—Shaft sealings using sealing-rings 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
    • F04D29/08—Sealings
    • F04D29/16—Sealings between pressure and suction sides
    • F04D29/161—Sealings between pressure and suction sides especially adapted for elastic fluid pumps
    • F04D29/162—Sealings between pressure and suction sides especially adapted for elastic fluid pumps of a centrifugal flow wheel
    • 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
    • F05D2240/00—Components
    • F05D2240/55—Seals
    • 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
    • F05D2240/00—Components
    • F05D2240/55—Seals
    • F05D2240/56—Brush seals

Definitions

  • the invention relates to a centrifugal compressor with at least one impeller mounted on a rotatably driven shaft in a compressor housing, which impeller has a front impeller and a rear impeller, the front impeller being provided with a number of moving blades for conveying a mass flow, the rear impeller of the impeller having blading , With the operation of the centrifugal compressor on the rear side of the impeller, a second pressure distribution is generated, which counteracts a first pressure distribution on the front side of the wheel in order to reduce an axial force to be supported in the compressor housing.
  • an impeller for a radial turbo compressor comprising a front side and a rear side of the wheel, the front side of the wheel being provided with a number of moving blades for conveying a medium, the rear side of the impeller having a number of blades , wherein the blades on the back of the impeller are shaped and arranged such that during operation of the centrifugal turbocompressor a second pressure distribution is generated by the blades on the back of the impeller which is identical to a first pressure distribution on the front of the impeller by less than ten percent deviates from the first pressure distribution in order to reduce an axial force to be supported on an axial bearing of the radial turbo compressor.
  • the object of the invention is to functionally improve a centrifugal compressor according to the preamble of claim 1, in particular with regard to use as an air supply device in a fuel cell system.
  • the task is in the case of a centrifugal compressor with at least one impeller mounted on a rotatably driven shaft in a compressor housing, which impeller has a front impeller and a rear impeller, the front impeller being provided with a number of moving blades for conveying a mass flow, the rear impeller of the impeller having blading has, with which a second pressure distribution is generated on the rear side of the impeller during operation of the centrifugal compressor, which counteracts a first pressure distribution on the front side of the wheel in order to reduce an axial force to be supported in the compressor housing, solved in that at a fluid passage between the shaft and a the housing part assigned to the rear of the wheel is provided with a flow resistance which is sufficiently large to minimize leakage flow and/or pressure equalization via the fluid passage.
  • the centrifugal compressor can also be referred to as a radial compressor.
  • the radial compressor is also referred to as a radial compressor.
  • the impeller is driven, for example, with the aid of an electric motor in order to compress a medium, in particular air, supplied on the front side of the wheel. Therefore, the compressor is also referred to as an air compressor or air compressor.
  • the air compressed by the air compressor is supplied to a cathode of a fuel cell.
  • the compressor can be connected in terms of drive to a turbine, which is driven by an exhaust gas from the fuel cell.
  • the impeller is attached to the shaft, which rotates about its axis of rotation during operation of the centrifugal compressor.
  • An axial direction is defined by the axis of rotation.
  • Axial means in the direction of or parallel to the axis of rotation of the impeller or shaft.
  • Analogously means radially across the axis of rotation of the impeller.
  • two radial bearings and one axial bearing are required to support the impeller with the shaft in the compressor housing.
  • German patent application DE 10 2018 215 068 A1 mentioned at the outset describes how the axial force to be supported with the axial bearing in the compressor housing is caused by the blading of the Impeller on the back of the wheel can be reduced or compensated.
  • the blading on the rear side of the impeller also performs this function in the claimed radial compressor.
  • a possibility for adjusting or further reducing the axial force is provided via the flow resistance.
  • a higher pressure occurs during operation on a side of the housing part assigned to the back of the wheel that faces away from the compressor wheel than on the side of the housing part assigned to the back of the wheel that faces the compressor wheel .
  • This pressure difference on the opposite sides of the housing part assigned to the rear side of the wheel leads to said leakage flow and/or said pressure equalization via the fluid passage.
  • the leakage flow and the pressure equalization over the fluid passage can be reduced, advantageously down to zero or close to zero.
  • the axial force to be supported on the compressor housing can be significantly reduced during operation of the centrifugal compressor. In this way, the drive power required for the back of the wheel blading can be reduced during operation.
  • a preferred exemplary embodiment of the radial compressor is characterized in that the flow resistance is arranged radially on the inside on the housing part assigned to the rear side of the wheel.
  • the measures described above and below can be applied individually or in any combination in order to adjust, in particular to increase, the flow resistance.
  • a further preferred exemplary embodiment of the radial compressor is characterized in that the flow resistance is arranged between a shaft shoulder and the housing part assigned to the rear side of the wheel.
  • the shaft shoulder simplifies the increase in flow resistance, in particular the attachment of a suitable sealing device.
  • a further preferred exemplary embodiment of the radial compressor is characterized in that the flow resistance involves a targeted reduction in the gap included at the fluid passage. In this case, an increased manufacturing effort is accepted in order to further reduce the drive power of the centrifugal compressor and thus the energy consumption in the operation of the rear impeller blading.
  • the flow resistance includes a resistance geometry on the shaft.
  • the flow resistance can be effectively increased, possibly even without an additional seal, by means of a corresponding resistance geometry, which is designed, for example, in the manner of a labyrinth.
  • a further preferred exemplary embodiment of the radial compressor is characterized in that the flow resistance comprises a resistance geometry on the housing part assigned to the rear side of the wheel.
  • the resistance geometry on the housing part assigned to the back of the wheel is particularly advantageously combined with the resistance geometry on the shaft.
  • the flow resistance includes a dynamic seal.
  • dynamic seal are, for example, a brush seal, a radial shaft seal, an axial shaft seal, a mechanical seal or a shaft lip seal.
  • the flow resistance includes a non-contact seal.
  • a non-contact seal This is, for example, a labyrinth seal.
  • the non-contact seal can also be designed as a magnetic fluid seal or as a chamber seal.
  • the object specified above is alternatively or additionally achieved in that the flow resistance at the fluid passage between the shaft and the housing part assigned to the back of the wheel minimizes the leakage flow and/or the pressure equalization via the fluid passage.
  • the invention also relates to a compressor housing, a housing part, a flow resistance, a seal and/or a shaft for a centrifugal compressor as described above. The parts mentioned can be traded separately.
  • the invention optionally also relates to a fuel cell system with a radial compressor as described above.
  • FIG. 2 shows a radial compressor similar to that in FIG. 1 according to a second exemplary embodiment with an optimized pressure distribution on the rear side of the wheel;
  • FIG. 3 shows an embodiment of the exemplary embodiment shown in FIG. 1 in longitudinal section
  • FIG. 4 shows a representation similar to that in FIG. 3 for the exemplary embodiment represented in FIG.
  • the compressor 1 comprises a compressor housing 2 in which an impeller 3 is rotatably mounted.
  • the impeller 3 is fastened to a shaft 4, which is only indicated on the left in FIGS. 1 and 2 and is cut off on the right.
  • the impeller 3 is driven by an electric motor via the shaft 4 .
  • a corresponding electric motor for driving the impeller 3 is preferably arranged to the right of the impeller 3 in FIGS.
  • the electric motor comprises, for example, a rotor which is connected to the shaft 4 in a rotationally fixed manner.
  • a turbine is arranged on the shaft 4, preferably on the right-hand end of the shaft 4 not shown in FIGS.
  • the impeller 3 On a front side 5 of the wheel, on the left in Figure 1, the impeller 3 includes moving blades 7. On a rear side 6 of the wheel, on the right in Figure 1, the impeller 3 includes blading 8, which is only indicated by hatching. An outer diameter of the moving blades 7 is indicated by an arrow 9 , In Figure 1 left, indicated on the wheel front 5. An outer diameter of the blading 8 of the impeller 3, on the right in FIG. 1, on the rear side 6 of the impeller is indicated by an arrow 10.
  • the rotor blades 7 on the front side 5 of the wheel and the blading 8 on the back side 6 of the wheel are designed in such a way that the pressure distributions 11, 12; 15.16 result.
  • the pressure distributions 11,12; 15,16 are each shown in a Cartesian coordinate diagram comprising an x-axis with the pressure and a y-axis with a radius of the impeller 3 in corresponding units.
  • a resulting axial force 13 is indicated by an arrow in FIG. Because of the pressure distribution 12, the resulting axial force 13 is relatively large.
  • the pressure distribution 12 on the back of the wheel 6 results from a Fluid passage with a relatively small flow resistance 14 between the shaft 4 and a housing part 20 assigned to the rear side of the wheel 6.
  • FIG. 2 uses pressure distributions 15, 16 to show how a resulting axial force 19 can be significantly reduced by a sufficiently large flow resistance 17 compared to FIG.
  • the flow resistance 17 includes a seal 18 between the shaft 4 and the housing part 20 assigned to the rear side of the wheel 6.
  • FIG. 4 indicates that the flow resistance 17 between the shaft 4 and the housing part 20 can be increased very effectively by a seal 25.
  • the seal 25 can effectively prevent an undesired passage of fluid from the fluid space 21 into the fluid space 22 .
  • the seal is designed, for example, as a labyrinth seal or as a brush seal.
  • the seal 25 can be positioned stably on a shaft shoulder 26 .

Landscapes

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

Abstract

L'invention concerne un compresseur radial (1) doté d'au moins une roue (3) qui est fixée sur un arbre entraîné en rotation (4) dans un carter de compresseur (2) et qui présente une face avant de roue (5) et une face arrière de roue (6). La face avant de roue (5) est pourvue d'un certain nombre de pales de roue (7) afin de transporter un flux massique, et la face arrière de roue (6) de la roue (3) présente un aubage (8), au moyen duquel une seconde répartition de pression (12) est générée sur la face arrière de roue (6) de la roue (3) pendant le fonctionnement du compresseur radial (1), ladite seconde répartition de pression s'opposant à une première répartition de pression (11) sur la face avant de roue (5) afin de réduire une force axiale à supporter dans le carter de compresseur. L'objectif de l'invention est d'améliorer fonctionnellement le compresseur radial (1), en particulier en ce qui concerne l'utilisation du compresseur radial en tant que dispositif d'alimentation en air dans un système de pile à combustible. Ceci est obtenu par le fait qu'une résistance à l'écoulement (14) est prévue au niveau d'un passage de fluide entre l'arbre (4) et une partie carter associée à la face arrière de roue (6), ladite résistance à l'écoulement étant suffisamment grande pour minimiser un écoulement de fuite et/ou une égalisation de pression par l'intermédiaire du passage de fluide.
PCT/EP2022/079508 2021-11-10 2022-10-24 Compresseur radial et procédé de fonctionnement d'un compresseur radial WO2023083588A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102021212662.6A DE102021212662A1 (de) 2021-11-10 2021-11-10 Radialverdichter und Verfahren zum Betreiben eines Radialverdichters
DE102021212662.6 2021-11-10

Publications (1)

Publication Number Publication Date
WO2023083588A1 true WO2023083588A1 (fr) 2023-05-19

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ID=84360702

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP2022/079508 WO2023083588A1 (fr) 2021-11-10 2022-10-24 Compresseur radial et procédé de fonctionnement d'un compresseur radial

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DE (1) DE102021212662A1 (fr)
WO (1) WO2023083588A1 (fr)

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4820115A (en) * 1987-11-12 1989-04-11 Dresser Industries, Inc. Open impeller for centrifugal compressors
JP2012251529A (ja) * 2011-06-07 2012-12-20 Daikin Industries Ltd 遠心圧縮機
KR20180115574A (ko) * 2017-04-13 2018-10-23 엘지전자 주식회사 터보 압축기
CN109083864A (zh) * 2018-07-27 2018-12-25 中国船舶重工集团公司第七〇九研究所 一种径流式旋转机械叶轮
DE102018215068A1 (de) 2018-09-05 2020-03-05 Robert Bosch Gmbh Laufrad für einen radialen Turboverdichter
US20200378389A1 (en) * 2017-03-29 2020-12-03 Mitsubishi Heavy Industries, Ltd. Electric supercharger

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4820115A (en) * 1987-11-12 1989-04-11 Dresser Industries, Inc. Open impeller for centrifugal compressors
JP2012251529A (ja) * 2011-06-07 2012-12-20 Daikin Industries Ltd 遠心圧縮機
US20200378389A1 (en) * 2017-03-29 2020-12-03 Mitsubishi Heavy Industries, Ltd. Electric supercharger
KR20180115574A (ko) * 2017-04-13 2018-10-23 엘지전자 주식회사 터보 압축기
CN109083864A (zh) * 2018-07-27 2018-12-25 中国船舶重工集团公司第七〇九研究所 一种径流式旋转机械叶轮
DE102018215068A1 (de) 2018-09-05 2020-03-05 Robert Bosch Gmbh Laufrad für einen radialen Turboverdichter

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