WO2011033800A1 - Compresseur centrifuge - Google Patents

Compresseur centrifuge Download PDF

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Publication number
WO2011033800A1
WO2011033800A1 PCT/JP2010/054505 JP2010054505W WO2011033800A1 WO 2011033800 A1 WO2011033800 A1 WO 2011033800A1 JP 2010054505 W JP2010054505 W JP 2010054505W WO 2011033800 A1 WO2011033800 A1 WO 2011033800A1
Authority
WO
WIPO (PCT)
Prior art keywords
flow path
annular shroud
impeller
forming portion
resin housing
Prior art date
Application number
PCT/JP2010/054505
Other languages
English (en)
Japanese (ja)
Inventor
誠一 茨木
勲 冨田
靖明 陣内
隆 御子神
正希 東條
明夫 北田
Original Assignee
三菱重工業株式会社
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 三菱重工業株式会社 filed Critical 三菱重工業株式会社
Priority to EP10816914A priority Critical patent/EP2441965A1/fr
Priority to CN2010800292137A priority patent/CN102472296A/zh
Priority to KR1020117031275A priority patent/KR20120013458A/ko
Priority to US13/380,649 priority patent/US20120148391A1/en
Publication of WO2011033800A1 publication Critical patent/WO2011033800A1/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
    • 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
    • F04D29/08—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
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/40—Casings; Connections of working fluid
    • F04D29/42—Casings; Connections of working fluid for radial or helico-centrifugal pumps
    • F04D29/4206—Casings; Connections of working fluid for radial or helico-centrifugal pumps 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
    • F04D29/40—Casings; Connections of working fluid
    • F04D29/42—Casings; Connections of working fluid for radial or helico-centrifugal pumps
    • F04D29/4206—Casings; Connections of working fluid for radial or helico-centrifugal pumps especially adapted for elastic fluid pumps
    • F04D29/4213—Casings; Connections of working fluid for radial or helico-centrifugal pumps especially adapted for elastic fluid pumps suction ports
    • 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
    • F04D29/40—Casings; Connections of working fluid
    • F04D29/42—Casings; Connections of working fluid for radial or helico-centrifugal pumps
    • F04D29/44—Fluid-guiding means, e.g. diffusers
    • F04D29/441—Fluid-guiding means, e.g. diffusers 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
    • F04D29/66—Combating cavitation, whirls, noise, vibration or the like; Balancing
    • F04D29/68—Combating cavitation, whirls, noise, vibration or the like; Balancing by influencing boundary layers
    • F04D29/681—Combating cavitation, whirls, noise, vibration or the like; Balancing by influencing boundary layers especially adapted for elastic fluid pumps
    • F04D29/685—Inducing localised fluid recirculation in the stator-rotor interface
    • 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
    • F05D2220/00—Application
    • F05D2220/40—Application in turbochargers
    • 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
    • F05D2250/00—Geometry
    • F05D2250/50—Inlet or outlet
    • F05D2250/52—Outlet
    • 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
    • F05D2300/00—Materials; Properties thereof
    • F05D2300/40—Organic materials
    • F05D2300/43—Synthetic polymers, e.g. plastics; Rubber
    • 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
    • F05D2300/00—Materials; Properties thereof
    • F05D2300/50—Intrinsic material properties or characteristics
    • F05D2300/502—Thermal properties
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10S—TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10S415/00—Rotary kinetic fluid motors or pumps

Definitions

  • the present invention relates to a centrifugal compressor provided with a resin housing applied to, for example, a turbocharger.
  • a turbocharger (exhaust turbine supercharger) mounted on an automobile or the like drives a compressor by an exhaust turbine driven by the energy of exhaust gas, and supplies intake air compressed by the compressor to the engine.
  • a bearing housing that rotatably supports a rotating shaft is provided between a turbine housing of an exhaust turbine and a housing of a turbo compressor.
  • An impeller of a turbo compressor and a wheel of an exhaust turbine are fixed to a rotating shaft passing through the bearing housing.
  • the bearing housing houses a bearing mechanism that rotatably supports the rotating shaft.
  • a seal wall is interposed at the boundary between the bearing housing and the compressor housing to form a compressed gas passage sealed in the compressor housing.
  • Patent Document 1 discloses that the turbocharger housing is made of a thermoplastic resin.
  • Patent Document 2 discloses a housing of a centrifugal compressor in which a housing wall is formed of two layers of a thermosetting resin material and a thermoplastic resin material.
  • an inner wall surface facing a flow path of a compressed gas in a compressor housing of a turbocharger is formed of a resin member having excellent machinability, and the curved inner surface of the compressor impeller and a curved profile portion of the compressor impeller are provided.
  • An invention has been disclosed in which the compressor efficiency is improved by reducing the gap between the impellers and the impeller (impeller) arranged facing the inner wall surface is prevented from being damaged even if the impeller contacts the inner wall surface. Yes.
  • Patent Document 4 discloses that an inner wall surface of a flow path forming portion of a compressor housing of a turbocharger is made of a resin member having excellent machinability for cost reduction.
  • Patent Document 5 discloses that, for the same reason as Patent Document 3, the inner wall surface of the flow path forming portion of the compressor housing of the turbocharger is made of a resin member.
  • FIG. 10 is a schematic diagram showing a compressor portion of the turbocharger 100 having a resin housing.
  • an impeller (impeller) 104 is fixed to the rotating shaft 102.
  • a plurality of blades 106 project radially from the impeller 104.
  • the outer end of the blade 106 forms a curved profile 106a.
  • a housing 110 is disposed around the blade 106.
  • the housing 110 includes a spiral volute portion 110a that forms the scroll portion s, and a flow path forming portion 110b that forms a flow path c of the compressed gas.
  • the flow path forming part 110b is disposed so as to surround the blade 106.
  • the hub surface 108 of the impeller 104 and the inner wall of the flow path forming portion 110b form a flow path c.
  • the flow path c is formed to be curved from the axial direction of the rotating shaft 102 (arrow a direction) to the radial direction of the impeller 104 (arrow b direction).
  • a flow path extending from the flow path c where the blade 106 is disposed to the flow path d disposed on the outlet side of the flow path c functions as a diffuser (static pressure increasing region).
  • the impeller 104 rotates, the compressed gas is sucked into the flow path c from the direction of the arrow a, and the absolute flow velocity is accelerated by the blade 106.
  • the intake air accelerated in the flow path c changes its direction in the direction of the arrow b, enters the area of the diffuser d, decelerates the absolute flow velocity, and increases the static pressure.
  • the compressed gas is compressed as it flows from the flow path c to the diffuser d, and flows out to the scroll portion s.
  • the compressor has higher compression efficiency when the gap T between the inner wall of the flow path forming portion 110b and the curved profile 106a of the impeller 104 is smaller.
  • the gas to be compressed becomes high temperature due to the compression action.
  • the housing 110 is made of resin, the resin has a higher coefficient of thermal expansion than that of metal, plastic, or the like. Therefore, the housing 110 is expanded by receiving the heat of the compressed gas, and as indicated by reference numeral 110 ′, the arrow e Causes thermal deformation in the direction. As a result, the gap T is enlarged, and the compressed gas leaks from the gap T, so that there is a problem that the compression efficiency is lowered.
  • German Patent Publication (DE10260042A1) European Patent Publication (EP1830071A2) JP-A-9-170442 Japanese Patent Laid-Open No. 2001-234753 JP 2002-256878 A
  • the present invention realizes a centrifugal compressor provided with a resin-made housing that does not reduce the compression efficiency and does not offset the advantages such as weight reduction and cost reduction. With the goal.
  • the centrifugal compressor of the present invention comprises: A plurality of blades radially fixed to the rotating shaft, and a resin housing disposed around the impeller, the outer peripheral surface of the impeller and the inner wall of the flow path forming portion of the resin housing
  • An annular shroud made of metal or ceramic material is disposed in a recess formed by engraving the inner wall of the flow path forming portion, and the outer surface of the flow path where the blade is disposed by the annular shroud and the outlet of the flow path Forming the outer surface of the diffuser (static pressure increasing region) arranged on the side,
  • the annular shroud is fixed to a surface or wall facing the annular shroud by the diffuser.
  • the inner wall of the flow path forming portion of the resin housing is engraved (or formed by injection molding) to form a recess, and an annular shroud made of metal or a ceramic material is disposed in the recess.
  • This annular shroud forms the smoothly curved outer surface of the flow path and diffuser.
  • the annular shroud is made of a material having a strength higher than that of a resin (engineering plastic stick) and a coefficient of thermal expansion smaller than that of the resin, such as a metal such as aluminum or carbon steel or ceramic. This annular shroud is fixed to the wall facing the diffuser.
  • the annular shroud is configured separately from the resin housing and is not joined to the inner wall of the resin housing. Therefore, since the thermal deformation of the resin housing is not transmitted to the annular shroud, the gap between the annular shroud and the curved profile of the impeller does not change. Therefore, the compression efficiency is not reduced. Further, by using the annular shroud, it is not necessary to increase the thickness of the resin housing or to provide the reinforcing rib on the resin housing, so that advantages such as weight reduction and cost reduction are not offset.
  • a seal ring may be provided in a receiving groove provided between the back surface of the annular shroud and the recess of the inner wall of the flow path forming portion in the inlet side region of the flow path.
  • the temperature of the compressed gas is low at the impeller inlet portion, the temperature of the inner wall of the annular shroud and the flow path forming part of the resin housing is also low. Therefore, an inexpensive seal ring such as a rubber O-ring can be used. Further, since the impeller inlet portion has a small radius, a small seal ring can be used, and the cost can be reduced accordingly.
  • the flow path forming portion of the resin housing may be divided and formed on the upstream side and the downstream side in the flow direction of the compressed gas, and the divided surface may be made to coincide with the receiving groove of the seal ring. .
  • the thick part of the resin housing can be eliminated.
  • the dividing surface is made coincident with the housing groove of the seal ring, the groove processing of the housing groove becomes unnecessary, so that the molding process becomes easy and the cost can be reduced.
  • a slit-shaped air gap is formed in the flow path forming portion of the resin housing or the divided body of the flow path forming portion so as to open to the outside in the axial direction of the rotating shaft.
  • a compressed gas circulation space is provided between the annular shroud and the flow path forming portion, and at least two communication holes communicating the flow space and the flow path along the flow direction of the compressed gas. It is good to comprise so that the flow of to-be-compressed gas may be formed in this circulation space.
  • a circulating flow path of the compressed gas that enters the flow space from the downstream through hole and returns to the flow path from the upstream through hole can be formed. Therefore, the flow rate at the inlet of the impeller can be maintained at a flow rate that is equal to or higher than the stall limit, so that the lower limit flow rate of the compressed gas can be reduced.
  • the outer surface of the flow path forming portion of the resin housing may be coated with an annular reinforcing layer made of glass fiber.
  • an annular reinforcing layer made of glass fiber having a high tensile strength, in the unlikely event that the blade breaks, the blade fragments or impellers do not penetrate the wall of the flow path forming part.
  • the wall thickness of the required flow path forming part can be reduced. Therefore, the manufacturing cost of the resin housing can be reduced.
  • an impeller having a plurality of blades fixed radially to a rotating shaft, and a resin housing disposed around the impeller, the outer peripheral surface of the impeller,
  • a centrifugal compressor in which a flow path of a compressed gas is formed from the inner wall of the flow path forming portion of the resin housing to the radial direction from the axial direction of the impeller, the inner wall of the flow path forming portion is engraved.
  • An annular shroud made of a metal or a ceramic material is disposed in the formed recess, and an outer surface of the flow path where the impeller is disposed by the annular shroud and an outer surface of the diffuser disposed on the outlet side of the flow path are formed.
  • the gap between the annular shroud and the curved profile of the blade can be maintained at a set size.
  • the annular shroud is disposed, so that it is not necessary to increase the thickness of the resin housing or to provide reinforcing ribs on the resin housing. And benefits such as cost reduction.
  • FIG. 1 is a front view according to a first embodiment of a turbocharger to which the present invention is applied. It is a front view which concerns on 2nd Embodiment of the turbocharger to which this invention is applied. It is a front view which concerns on 3rd Embodiment of the turbocharger to which this invention is applied. It is a front view which concerns on 4th Embodiment of the turbocharger to which this invention is applied. It is a front view which concerns on 5th Embodiment of the turbocharger to which this invention is applied. It is a front view which shows the modification of the said 5th Embodiment. It is a front view which concerns on 6th Embodiment of the turbocharger to which this invention is applied.
  • FIG. 1 shows a part of a compressor section of a turbocharger 10 according to this embodiment.
  • a rotating shaft 12 is disposed at the center of a resin housing 20, and an impeller 14 in which a plurality of blades 16 are radially disposed in the radial direction of the rotating shaft 12 is fixedly provided on the outer peripheral surface of the rotating shaft 12.
  • the hub surface 18 of the impeller 14 is curved from the axial direction of the rotating shaft 12 toward the radial direction from the inlet side to the outlet side in the flow direction (arrow a direction) of the compressed gas.
  • the resin housing 20 includes a spiral volute portion 20a that forms a scroll portion s therein, and a flow path forming portion 20b that forms a flow path c of a compressed gas.
  • the outer end of the blade 16 forms a curved profile 16a.
  • inner wall 20b 1 flow path forming portion 20b of the resin housing 20 are formed.
  • a concave portion 20b 2 for inserting and arranging the annular shroud 22 is formed in the inner wall 20b 1 .
  • the rotary shaft 12 is rotatably supported by a bearing (not shown) provided in the bearing housing 30.
  • a partition wall 32 forming a part of the bearing housing 30 is arranged facing the scroll part s formed by the spiral volute part 20a.
  • An end portion of the volute portion 20 a is attached to the partition wall 32 via a seal ring 34.
  • annular shroud 22 is inserted and disposed in the recess 20b 2 formed in the inner wall 20b 1 of the flow path forming portion 20b.
  • the downstream end portion of the annular shroud 22 in the flow direction of the compressed gas protrudes from the scroll portion s, and the downstream end portion is fixed to the wall 32 by the bolt 26 via the spacer 24.
  • the annular shroud 22 is made of a metal (for example, aluminum or carbon steel) or ceramics having a strength higher than that of the resin and a coefficient of thermal expansion smaller than that of the resin.
  • the annular shroud 22 is separated from the resin housing 20 and is not connected.
  • the gap between the annular shroud 22 and the curved profile 16a of the blade 16 is set to be as small as possible in order to maintain good compression efficiency.
  • the annular shroud 22 is arranged on the flow path c for directing the compressed gas from the axial direction (arrow a direction) to the radial direction (arrow b direction) of the impeller 14 and on the outlet side of the flow path c.
  • An outer wall of the diffuser d that converts kinetic energy into static pressure is formed.
  • the hub surface 18 of the impeller 14 forms the inner surface of the flow path c
  • the partition wall 32 forms the inner surface of the diffuser d.
  • the gas to be compressed is sucked from the inlet side of the blade 16 by the rotation of the impeller 14, and is converted into a static pressure through the flow path c and the diffuser d.
  • the compressed gas exiting the diffuser d flows out to the scroll part s.
  • a plurality of bolts 26 are arranged at intervals in the circumferential direction of the rotating shaft 12, and the presence of the bolts 26 does not hinder the flow of the compressed gas.
  • the annular shroud 22 is fixed to the bearing housing 30 partition wall 32 with only the bolts 26, and the annular shroud 22 and the resin housing 20 are separated from each other.
  • the thermal deformation of the housing 20 is not transmitted. Therefore, even when the resin housing 20 is thermally deformed, the gap between the annular shroud 22 and the curved profile 16a of the blade 16 does not change. Therefore, the compression efficiency is not lowered.
  • annular shroud 22 since the annular shroud 22 is used, there is no need to increase the thickness of the resin housing 20 or to provide a reinforcing rib or the like on the resin housing 20, so that advantages such as weight reduction and cost reduction are offset. None happen.
  • the downstream end 22 a of the annular shroud 22 forms two bent portions and extends until it contacts the partition wall 32 of the bearing housing 30.
  • Flange 22a 1 is formed on the extension end portion.
  • the recess 32a for fitting the flange portion 22a 1 is engraved in the partition wall 32. Then, the flange portion 22a 1 are connected by bolts 40 to the recess 32a.
  • the flange portion 22a 1 is partially formed in the circumferential direction of the impeller 14, therefore, not to close the diffuser d at the downstream side end portion 22a of the shroud 22, of the compressed gas in the diffuser d Does not obstruct the flow.
  • Other configurations are the same as those of the first embodiment. The same parts are denoted by the same reference numerals.
  • annular shroud 22 forms the integral structure to the flange portion 22a 1, and is processed by press molding. Therefore, in addition to the operational effects obtained in the first embodiment, the annular shroud 22 can be easily molded, and when the annular shroud 22 is connected to the partition wall 32, the spacer 24 is used as in the first embodiment. There is an advantage that the connecting work becomes easy.
  • a storage groove 52 is formed in the recess 20b 2 formed in the inner wall 20b 1 of the flow path forming portion 20b of the resin housing 20, and the storage is performed.
  • a rubber or resin seal ring 50 is accommodated in the groove 52.
  • Other configurations are the same as those of the second embodiment.
  • the seal ring 50 even when the resin housing 20 is thermally deformed and a gap is generated between the recess 20b 2 and the back surface of the annular shroud 2 (made of metal or ceramic such as aluminum or carbon steel), by providing the seal ring 50, since the compressed gas from entering between the recess 20b 2 and the annular shroud 22, the compression efficiency of the compressor is not lowered.
  • the temperature of the compressed gas is substantially the same as that of the outside air, and the temperature of the compressed gas is low.
  • an inexpensive O-ring made of rubber can be used at the inlet portion of the impeller 14.
  • the inlet portion of the impeller 14 can use a small-diameter O-ring because the flow path of the compressed gas is not curved in the radial direction and the diameter of the impeller 14 is small. Therefore, the cost of the seal ring 50 can be reduced. (Embodiment 4)
  • the flow path forming portion 20 b of the resin housing 20 is divided into two resin divided bodies 60 and 62.
  • the divided bodies 60 and 62 are divided and formed by a dividing surface 64 having a stepped portion 64a at the center of the thick portion of the flow path forming portion 20b.
  • One end of the dividing surface 64 is connected to the accommodation groove 52 that accommodates the seal ring 34.
  • Other configurations are the same as those of the third embodiment.
  • the thickness of the flow path forming portion 20b can be reduced. This eliminates the possibility that bubbles or the like remain in the flow path forming portion 20b during the molding process of the resin housing 20. Therefore, the quality of the resin housing 20 is improved and the yield can be improved, so that the manufacturing cost of the resin housing 20 can be reduced. Moreover, since the dividing surface 64 is connected to the receiving groove 52, the groove processing of the receiving groove 52 becomes unnecessary, and the corner portion of the divided body 60 is processed. Can be saved. (Embodiment 5)
  • a slit-like gap is formed in the thick portion of the flow path forming portion 20 b of the resin housing 20 in a direction perpendicular to the plate thickness direction, that is, in a direction substantially parallel to the rotation direction of the impeller 14.
  • V is provided. One end of the gap V is open to the outside.
  • Other configurations are the same as those of the third embodiment.
  • the gap V in the flow path forming part 20b by providing the gap V in the flow path forming part 20b, the thick part of the flow path forming part 20b can be eliminated. For this reason, bubbles and the like are not left during the injection molding of the resin housing 20, the quality of the resin housing 20 can be improved, and the yield can be improved, so that an increase in cost can be prevented.
  • the present modified example includes, among the divided bodies 60 and 62 in which the resin housing 20 is divided and formed in the fourth embodiment, inside the thick portion that forms the flow path forming portion 20 b of the divided body 60.
  • a slit-shaped gap Va is provided in a direction perpendicular to the plate thickness direction (a direction substantially parallel to the rotation direction of the impeller 14). One end of the gap Va is open to the outside.
  • Other configurations are the same as those of the fourth embodiment.
  • the slit-shaped gap Va is provided in the flow path forming portion 20b of the divided body 60. It can be lost. For this reason, bubbles and the like do not remain at the time of injection molding of the divided body 60, the quality of the divided body 60 can be improved, and the yield can be improved, thereby preventing an increase in cost. (Embodiment 6)
  • a recess 20 b 2 formed on the inner wall 20 b 1 of the flow path forming portion 20 b is further formed so as to form a circulation flow path 70 on the back side of the annular shroud 22. is doing.
  • An upstream through hole 72 and a downstream through hole 74 are formed in the annular shroud 22 at a position facing the circulation flow path 70.
  • Other configurations are the same as those of the second embodiment.
  • the flow rate of the compressed gas when the flow rate of the compressed gas is small, a part of the compressed gas flowing through the flow path c flows into the circulation flow path 70 from the downstream through hole 74 and flows into the circulation flow path 70.
  • a circulating flow in which the compressed gas returns from the upstream through hole 72 to the flow path c can be formed.
  • the circulation flow is added to the flow of the compressed gas at the inlet of the impeller 14, so that the stall of the impeller 14 can be suppressed. Therefore, the limit lower limit flow rate of the compressor can be reduced.
  • the flow rate of the compressed gas when the flow rate of the compressed gas is large, a part of the compressed gas flowing through the flow path c flows into the circulation flow path 70 from the upstream side through-hole 72, and the compressed gas flowing into the circulation flow path 70 flows downstream. A flow path returning from the through hole 74 to the flow path c can be formed. As a result, the maximum flow rate of the compressed gas can be increased. As a result, the flow width of the compressed gas that can operate the turbocharger can be expanded.
  • the present modification is one in which a circulation channel 70 is formed on the back surface of the annular shroud 22 as in the sixth embodiment.
  • An annular slit 76 is formed between the inlet side end of the annular shroud 22 and the inner wall 20b1 of the passage forming portion 20b at the inlet portion of the passage c.
  • a through hole 74 similar to that of the sixth embodiment is provided on the downstream side of the slit-shaped gap 76.
  • Other configurations are the same as those of the sixth embodiment.
  • the number of through holes drilled in the annular shroud 22 can be reduced as compared with the sixth embodiment, and the recess for fitting the annular shroud 22 to the inner wall 20a of the flow path forming portion 20b. Since there is no need to engrave 20b 2 , there is an advantage that the processing of the annular shroud 22 and the flow path forming portion 20b becomes easy. Further, since the annular slit-shaped gap 76 can be formed, the opening area of the slit-shaped gap 76 can be increased, and the slit-shaped gap 76 can be easily formed.
  • the flow passage forming portion 20b of the resin housing 20 is formed with a thin plate thickness, and an annular glass fiber plate 80 is attached to the back surface thereof.
  • Other configurations are the same as those of the second embodiment.
  • the thickness of the flow path forming portion 20b can be reduced. Further, since the thickness of the flow path forming portion 20b can be reduced, bubbles or the like do not remain at the time of injection molding of the resin housing 20, and the quality of the resin housing 20 can be improved. Therefore, the yield at the time of resin housing molding processing can be improved, and cost increase can be prevented.

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

Abstract

L'invention porte sur un compresseur centrifuge comportant un corps en résine, qui est fait de telle manière que le rendement de compression n'est pas perdu et que les avantages tels que la réduction du poids et du coût ne sont pas annulés. Un turbocompresseur (10) comporte un corps en résine (20) qui comprend une section en volute (20a) et une section de formation de canaux (20b), et une roue à aubes (14) qui est fixée, au centre de la section de formation de canaux (20b), à un arbre rotatif (12). Une enveloppe annulaire (22) est disposée dans une cavité (20b2) formée sur la paroi intérieure (20b1) de la section de formation de canaux (20b), et l'enveloppe annulaire (22) forme les parois extérieures d'un canal (c) et d'un diffuseur (une région d'accroissement de la pression statique) (d) pour le gaz comprimé. Le bord de l'enveloppe annulaire (22) sur le côté aval est fixé par l'intermédiaire d'une entretoise (24) à une cloison (32) qui forme une partie d'un boîtier de palier (30), au moyen d'une vis (26). Même si le corps en résine (20) subit une déformation thermique, les dimensions d'un espace libre (T) entre l'enveloppe annulaire (22) et le profil courbe (16a) d'une aube (16) peuvent être maintenues à des dimensions fixées.
PCT/JP2010/054505 2009-09-16 2010-03-17 Compresseur centrifuge WO2011033800A1 (fr)

Priority Applications (4)

Application Number Priority Date Filing Date Title
EP10816914A EP2441965A1 (fr) 2009-09-16 2010-03-17 Compresseur centrifuge
CN2010800292137A CN102472296A (zh) 2009-09-16 2010-03-17 离心压缩机
KR1020117031275A KR20120013458A (ko) 2009-09-16 2010-03-17 원심 압축기
US13/380,649 US20120148391A1 (en) 2009-09-16 2010-03-17 Centrifugal compressor

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2009-215082 2009-09-16
JP2009215082A JP2011064118A (ja) 2009-09-16 2009-09-16 遠心圧縮機

Publications (1)

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WO2011033800A1 true WO2011033800A1 (fr) 2011-03-24

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Country Status (6)

Country Link
US (1) US20120148391A1 (fr)
EP (1) EP2441965A1 (fr)
JP (1) JP2011064118A (fr)
KR (1) KR20120013458A (fr)
CN (1) CN102472296A (fr)
WO (1) WO2011033800A1 (fr)

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GB2493973A (en) * 2011-08-26 2013-02-27 Dyson Technology Ltd Rotor assembly with shroud mounted on bearing
CN102996520A (zh) * 2012-12-27 2013-03-27 中国航空工业集团公司金城南京机电液压工程研究中心 一种离心压气机壳体结构
US9169843B2 (en) 2011-08-26 2015-10-27 Dyson Technology Limited Turbomachine
US9410442B2 (en) 2011-08-26 2016-08-09 Dyson Technology Limited Turbomachine
US9410553B2 (en) 2011-08-26 2016-08-09 Dyson Technology Limited Rotor assembly for a turbomachine

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DE102012211375A1 (de) * 2012-06-29 2014-04-10 Bayerische Motoren Werke Aktiengesellschaft Abgasturbolader
US9200639B2 (en) 2012-08-19 2015-12-01 Honeywell International Inc. Compressor housing assembly
DE102014204768A1 (de) * 2013-05-16 2014-11-20 Bosch Mahle Turbo Systems Gmbh & Co. Kg Radialverdichter für einen Abgasturbolader
KR101537061B1 (ko) * 2013-06-10 2015-07-15 정현욱 모터 및 이를 구비한 터보 압축기
CN106662118B (zh) 2014-07-02 2019-05-28 三菱重工业株式会社 压气机
KR101634876B1 (ko) * 2014-12-02 2016-06-30 한국기계연구원 열응력으로 인한 손상 방지구조를 갖는 초소형 가스터빈
JP6270280B2 (ja) * 2014-12-03 2018-01-31 三菱重工業株式会社 インペラ、及び回転機械
JP6288516B2 (ja) * 2014-12-03 2018-03-07 三菱重工業株式会社 インペラ、及び回転機械
JP6204398B2 (ja) * 2015-03-23 2017-09-27 カルソニックカンセイ株式会社 タービンハウジング
US10400790B2 (en) 2015-05-21 2019-09-03 Mitsubishi Heavy Industries Compressor Corporation Compressor
CN108350797B (zh) * 2015-11-06 2020-07-03 康奈可关精株式会社 涡轮壳
WO2018111457A1 (fr) 2016-12-14 2018-06-21 Carrier Corporation Compresseur centrifuge à deux étages
JP7164346B2 (ja) * 2018-07-24 2022-11-01 三菱重工マリンマシナリ株式会社 回転機械及び過給機
JP2020023917A (ja) * 2018-08-07 2020-02-13 株式会社オティックス 過給機用のコンプレッサハウジング
DE102018128255A1 (de) * 2018-11-12 2020-05-14 Ebm-Papst Landshut Gmbh Gebläsevorrichtung
EP3904697A1 (fr) * 2020-04-29 2021-11-03 ABB Schweiz AG Silencieux pour un turbocompresseurs d'un moteur à combustion interne
US11519423B1 (en) * 2021-11-11 2022-12-06 Progress Rail Locomotive Inc. Compressor joint
JP2023080448A (ja) * 2021-11-30 2023-06-09 株式会社豊田自動織機 ターボ式流体機械

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Publication number Priority date Publication date Assignee Title
GB2493973A (en) * 2011-08-26 2013-02-27 Dyson Technology Ltd Rotor assembly with shroud mounted on bearing
GB2493973B (en) * 2011-08-26 2015-04-15 Dyson Technology Ltd Rotor assembly for a turbomachine
US9169843B2 (en) 2011-08-26 2015-10-27 Dyson Technology Limited Turbomachine
US9410442B2 (en) 2011-08-26 2016-08-09 Dyson Technology Limited Turbomachine
US9410553B2 (en) 2011-08-26 2016-08-09 Dyson Technology Limited Rotor assembly for a turbomachine
US9863429B2 (en) 2011-08-26 2018-01-09 Dyson Technology Limited Rotor assembly for a turbomachine
US11668322B2 (en) 2011-08-26 2023-06-06 Dyson Technology Limited Turbomachine
CN102996520A (zh) * 2012-12-27 2013-03-27 中国航空工业集团公司金城南京机电液压工程研究中心 一种离心压气机壳体结构

Also Published As

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CN102472296A (zh) 2012-05-23
US20120148391A1 (en) 2012-06-14
JP2011064118A (ja) 2011-03-31
KR20120013458A (ko) 2012-02-14
EP2441965A1 (fr) 2012-04-18

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