WO2022107519A1 - Compresseur centrifuge et compresseur de suralimentation - Google Patents

Compresseur centrifuge et compresseur de suralimentation Download PDF

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Publication number
WO2022107519A1
WO2022107519A1 PCT/JP2021/038265 JP2021038265W WO2022107519A1 WO 2022107519 A1 WO2022107519 A1 WO 2022107519A1 JP 2021038265 W JP2021038265 W JP 2021038265W WO 2022107519 A1 WO2022107519 A1 WO 2022107519A1
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WO
WIPO (PCT)
Prior art keywords
flow path
main flow
impeller
compressor
upstream
Prior art date
Application number
PCT/JP2021/038265
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English (en)
Japanese (ja)
Inventor
薫哉 角舘
克典 時枝
隆 藤原
隆弘 馬場
Original Assignee
株式会社Ihi
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 株式会社Ihi filed Critical 株式会社Ihi
Publication of WO2022107519A1 publication Critical patent/WO2022107519A1/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
    • F04D29/66—Combating cavitation, whirls, noise, vibration or the like; Balancing

Definitions

  • a centrifugal compressor includes a compressor housing.
  • Patent Document 1 discloses a compressor housing in which a main flow path and a sub flow path are formed.
  • a compressor impeller is arranged in the main flow path.
  • the sub flow path is arranged radially outside the main flow path.
  • the main flow path and the sub flow path communicate with each other through the upstream slit and the downstream slit.
  • the flow rate of the air passing through the compressor impeller is smaller than the predetermined flow rate, the air compressed by the compressor impeller flows into the sub-flow path through the downstream slit and flows out to the main flow path through the upstream slit. In this way, the apparent flow rate of air flowing through the main flow path increases, so that the working region on the small flow rate side of the centrifugal compressor expands.
  • the air flowing in the main flow path flows along the rotation axis direction of the compressor impeller.
  • the air flowing out from the upstream slit to the main flow path pushes the fluid flowing in the main flow path in the radial direction.
  • the actual outer diameter of the main flow path is narrowed down, which causes a decrease in compressor efficiency.
  • An object of the present disclosure is to provide a centrifugal compressor and a turbocharger capable of suppressing a decrease in compressor efficiency.
  • the centrifugal compressor includes a main flow path in which an impeller is arranged, a sub flow path formed radially outside the impeller from the main flow path, and an impeller and a radial direction.
  • a downstream communication passage that is arranged facing the main flow path and connects the main flow path and the sub flow path, and an upstream communication path that is separated from the impeller by the downstream communication flow path and connects the main flow path and the sub flow path. It comprises an opening connected to the road, the end face of the opening comprising an upstream communication passage directed to the impeller.
  • the end face may be oriented in the direction of the rotation axis of the impeller.
  • the upstream communication passage may include a communication portion having a flow path cross section smaller than the flow path cross section of the downstream communication passage.
  • the upstream communication passage may include a first communication portion extending inward in the radial direction and a second communication portion extending in a direction close to the impeller.
  • the turbocharger includes the above-mentioned centrifugal compressor.
  • FIG. 1 is a schematic cross-sectional view of the turbocharger.
  • FIG. 2 is an extraction diagram of the alternate long and short dash line portion of FIG.
  • FIG. 1 is a schematic cross-sectional view of the turbocharger TC.
  • the arrow L direction shown in FIG. 1 will be described as the left side of the turbocharger TC.
  • the arrow R direction shown in FIG. 1 will be described as the right side of the turbocharger TC.
  • the supercharger TC includes a supercharger main body 1.
  • the turbocharger main body 1 includes a bearing housing 3, a turbine housing 5, and a compressor housing 7.
  • a turbine housing 5 is connected to the left side of the bearing housing 3 by a fastening bolt 9.
  • a compressor housing 7 is connected to the right side of the bearing housing 3 by a fastening bolt 11.
  • the turbocharger TC of the present embodiment includes a turbine T and a centrifugal compressor C.
  • the turbine T includes a bearing housing 3 and a turbine housing 5.
  • the centrifugal compressor C includes a bearing housing 3 and a compressor housing 7.
  • the centrifugal compressor C may be incorporated in a device other than the turbocharger TC, or may be a single unit.
  • a bearing hole 3a is formed in the bearing housing 3.
  • the bearing hole 3a penetrates the bearing housing 3 in the left-right direction of the turbocharger TC.
  • a bearing 13 is provided in the bearing hole 3a.
  • FIG. 1 shows a fully floating bearing as an example of the bearing 13.
  • the bearing 13 may be another radial bearing such as a semi-floating bearing or a rolling bearing.
  • the shaft 15 is rotatably supported by the bearing 13.
  • a turbine impeller 17 is provided at the left end of the shaft 15.
  • the turbine impeller 17 is rotatably housed in the turbine housing 5.
  • a compressor impeller (impeller) 19 is provided at the right end of the shaft 15.
  • the compressor impeller 19 is rotatably housed in the compressor housing 7.
  • the axial direction, the radial direction and the circumferential direction of the shaft 15, the turbine impeller 17 and the compressor impeller 19 may be simply referred to as the rotational axis direction, the radial direction and the circumferential direction, respectively, unless otherwise specified.
  • a housing hole 7a is formed in the compressor housing 7.
  • the housing hole 7a opens on the right side of the turbocharger TC.
  • the mounting member 21 is connected to the housing hole 7a.
  • the mounting member 21 is configured separately from the compressor housing 7.
  • the mounting member 21 is press-fitted into the housing hole 7a.
  • the present invention is not limited to this, and the mounting member 21 may be adhered to or welded to the housing hole 7a.
  • a male screw may be formed on the outer peripheral surface of the mounting member 21, a female screw may be formed on the inner peripheral surface of the housing hole 7a, and the mounting member 21 may be fastened to the housing hole 7a.
  • the mounting member 21 has a cylindrical shape. The mounting member 21 is mounted on the inner peripheral surface of the housing hole 7a.
  • the main flow path 23 is formed by the housing hole 7a and the inner peripheral surface of the mounting member 21.
  • the main flow path 23 opens on the right side of the turbocharger TC.
  • the main flow path 23 extends in the direction of the rotation axis.
  • the compressor impeller 19 is arranged in the main flow path 23.
  • the main flow path 23 is connected to an air cleaner (not shown).
  • a diffuser flow path 25 is formed between the bearing housing 3 and the compressor housing 7.
  • the diffuser flow path 25 is formed by surfaces facing each other in the rotation axis direction of the bearing housing 3 and the compressor housing 7.
  • the diffuser flow path 25 pressurizes air.
  • the diffuser flow path 25 is formed in an annular shape from the inside to the outside in the radial direction.
  • the diffuser flow path 25 communicates with the main flow path 23 on the inner side in the radial direction.
  • a compressor scroll flow path 27 is formed in the compressor housing 7.
  • the compressor scroll flow path 27 is formed in an annular shape.
  • the compressor scroll flow path 27 is located radially outside the diffuser flow path 25, for example.
  • the compressor scroll flow path 27 communicates with an engine intake port and a diffuser flow path 25 (not shown).
  • a fluid for example, air
  • the intake fluid is pressurized and accelerated as it passes between the blades of the compressor impeller 19.
  • the pressure-accelerated fluid is further pressurized in the diffuser flow path 25 and the compressor scroll flow path 27.
  • the pressurized fluid is guided to the intake port of the engine.
  • a discharge port 29 is formed in the turbine housing 5.
  • the discharge port 29 opens on the left side of the turbocharger TC.
  • the discharge port 29 is connected to an exhaust gas purification device (not shown).
  • the turbine housing 5 is formed with a communication passage 31 and a turbine scroll flow path 33.
  • the communication passage 31 is located radially outside the turbine impeller 17.
  • the communication passage 31 connects the turbine scroll flow path 33 and the discharge port 29 via the turbine impeller 17.
  • the turbine scroll flow path 33 is formed in an annular shape.
  • the turbine scroll passage 33 is located radially outside the communication passage 31, for example.
  • the turbine scroll flow path 33 communicates with a gas inlet (not shown).
  • Exhaust gas discharged from an engine exhaust manifold (not shown) is guided to the gas inlet.
  • the exhaust gas guided from the gas inlet to the turbine scroll flow path 33 is guided to the discharge port 29 via the communication passage 31 and between the blades of the turbine impeller 17.
  • the exhaust gas guided to the discharge port 29 rotates the turbine impeller 17.
  • the rotational force of the turbine impeller 17 is transmitted to the compressor impeller 19 via the shaft 15.
  • the fluid (air) is pressurized by the rotational force of the compressor impeller 19 and guided to the intake port of the engine.
  • FIG. 2 is an extraction diagram of the alternate long and short dash line portion of FIG.
  • a circulation flow path 100 is formed in the compressor housing 7.
  • the circulation flow path 100 includes a sub-flow path 110, an upstream communication passage 120, and a downstream communication passage 130.
  • the arrow R direction shown in FIG. 2 will be described as the upstream side in the intake flow of the main flow path 23.
  • the arrow L direction shown in FIG. 2 will be described as the downstream side in the intake air flow of the main flow path 23.
  • the upstream side and the downstream side in the intake air flow of the main flow path 23 may be simply referred to as the upstream side and the downstream side, respectively, unless otherwise specified.
  • the sub flow path 110 is formed radially outside the main flow path 23.
  • the sub-flow path 110 is formed apart from the main flow path 23 in the radial direction.
  • the auxiliary flow path 110 extends in the circumferential direction and is formed in a substantially cylindrical shape.
  • the upstream continuous passage 120 and the downstream continuous passage 130 are formed between the sub flow path 110 and the main flow path 23.
  • the upstream communication passage 120 and the downstream communication passage 130 connect the main flow path 23 and the sub flow path 110.
  • the upstream passage 120 is separated from the compressor impeller 19 more than the downstream passage 130.
  • the upstream passage 120 is located on the upstream side (on the right side in FIG. 2) of the leading edge LE, which is the leading edge of the compressor impeller 19. The details of the shape of the upstream passage 120 will be described later.
  • the downstream passage 130 is closer to the compressor impeller 19 than the upstream passage 120.
  • the downstream passage 130 is located on the downstream side (left side in FIG. 2) of the leading edge LE of the compressor impeller 19.
  • the downstream passage 130 is arranged so as to face the compressor impeller 19 in the radial direction.
  • the downstream passage 130 is formed in a roughly annular shape.
  • the downstream passage 130 extends radially.
  • a partition wall 140 is formed between the main flow path 23, the sub-flow path 110, the upstream continuous passage 120, and the downstream continuous passage 130.
  • the partition wall 140 is provided between the main flow path 23 and the sub flow path 110 in the radial direction.
  • the partition wall 140 partitions the main flow path 23 and the sub flow path 110.
  • the partition wall 140 is provided between the upstream communication passage 120 and the downstream communication passage 130 in the rotation axis direction.
  • the partition wall 140 partitions the upstream continuous passage 120 and the downstream continuous passage 130.
  • the partition wall 140 is configured separately from the mounting member 21.
  • the partition wall 140 has a cylindrical shape.
  • the partition wall 140 has an inclined portion 141 on the end face on the upstream side.
  • the inclined portion 141 is a surface that is inclined inward in the radial direction toward the downstream side with respect to a surface orthogonal to the rotation center axis of the compressor impeller 19.
  • the inner peripheral surface of the partition wall 140 includes a large-diameter portion 143, a tapering portion 145, and a small-diameter portion 147.
  • the large diameter portion 143 is located radially inside the inclined portion 141.
  • the upstream end of the large diameter portion 143 is continuous with the inclined portion 141, and the downstream end is continuous with the tapering portion 145.
  • the large diameter portion 143 has a substantially constant inner diameter.
  • the upstream end of the tapering portion 145 is continuous with the large diameter portion 143, and the downstream end is continuous with the small diameter portion 147.
  • the inner diameter of the gradually decreasing portion 145 gradually decreases from the upstream side to the downstream side.
  • the inner diameter of the upstream end of the tapering portion 145 is equal to the inner diameter of the large diameter portion 143.
  • the inner diameter of the downstream end of the tapering portion 145 is equal to the inner diameter of the small diameter portion 147.
  • the upstream end of the small diameter portion 147 is continuous with the tapering portion 145, and the downstream end is continuous with the downstream end face of the partition wall 140.
  • the small diameter portion 147 has a substantially constant inner diameter.
  • the inner diameter of the small diameter portion 147 is smaller than the inner diameter of the large diameter portion 143.
  • the partition wall 140 is not limited to this, and the partition wall 140 may not be provided with the inclined portion 141, the large diameter portion 143, the tapering portion 145, and the small diameter portion 147.
  • the upstream end face of the partition wall 140 may be a plane orthogonal to the rotation center axis of the compressor impeller 19.
  • the inner peripheral surface of the partition wall 140 may be a parallel portion having a substantially constant inner diameter from the upstream side to the downstream side.
  • a rib 150 is provided in the auxiliary flow path 110.
  • the rib 150 is formed in a plate shape, for example.
  • the rib 150 extends in the direction of the rotation axis.
  • a plurality of ribs 150 are provided in the auxiliary flow path 110.
  • the plurality of ribs 150 are spaced apart from each other and arranged at equal intervals in the circumferential direction.
  • the plurality of ribs 150 may be arranged at irregular intervals in the circumferential direction.
  • the rib 150 is connected to the compressor housing 7 and the partition wall 140.
  • the rib 150 supports (holds) the partition wall 140 so as not to fall off from the compressor housing 7.
  • the partition wall 140 is formed separately from the compressor housing 7.
  • the present invention is not limited to this, and the partition wall 140 may be integrally formed with the compressor housing 7. In that case, the partition wall 140, the rib 150, and the compressor housing 7 are integrally formed.
  • the mounting member 21 has an inclined portion 21a on a surface facing the inclined portion 141 of the partition wall 140 in the direction of the rotation axis.
  • the inclined portion 21a is separated from the inclined portion 141 of the partition wall 140 in the rotation axis direction.
  • the inclined portion 21a is a surface that is inclined inward in the radial direction toward the downstream side with respect to a surface orthogonal to the rotation center axis of the compressor impeller 19.
  • the inclined direction of the inclined portion 21a is the same as the inclined direction of the inclined portion 141 of the partition wall 140.
  • the inclination angles of the inclined portions 21a and 141 are substantially equal to each other.
  • the mounting member 21 is not limited to this, and the mounting member 21 may not be provided with the inclined portion 21a.
  • the surface of the mounting member 21 facing the inclined portion 141 of the partition wall 140 in the rotation axis direction may be a surface orthogonal to the rotation center axis of the compressor impeller 19.
  • the mounting member 21 includes the extending portion 21b.
  • the inclined portion 21a extends radially inward from the large diameter portion 143 of the partition wall 140. A part of the inclined portion 21a is located radially inside the large diameter portion 143 of the partition wall 140.
  • the extending portion 21b is continuous with the radially inner end portion of the inclined portion 21a.
  • the extending portion 21b extends downstream from the inclined portion 21a toward the compressor impeller 19.
  • the extending portion 21b has a cylindrical shape.
  • the extending portion 21b extends in the rotation axis direction from the inclined portion 21a toward the downstream side.
  • the extending portion 21b may extend in a direction inclined with respect to the rotation axis direction toward the downstream side from the inclined portion 21a.
  • the extending portion 21b extends in a direction (downstream side) close to the compressor impeller 19.
  • the extending portion 21b is located radially inside the large diameter portion 143 of the partition wall 140. A part of the extending portion 21b faces the large diameter portion 143 in the radial direction. The extending portion 21b is separated radially inward from the large diameter portion 143. The extending portion 21b is located radially outside the small diameter portion 147 of the partition wall 140. However, the extending portion 21b is not limited to this, and the inner diameter of the extending portion 21b may be equal to the inner diameter of the small diameter portion 147 or may be smaller than the inner diameter of the small diameter portion 147.
  • an end face 21c of the opening PP connected to the main flow path 23 is formed at the downstream end of the extending portion 21b.
  • the opening PP includes an end surface 21c of the extending portion 21b and an inner diameter side opening P2 of the upstream communication passage 120 described later. The end face 21c and the inner diameter side opening P2 are formed on the same plane.
  • An upstream continuous passage 120 is formed between the inclined portion 141 and the large diameter portion 143 of the partition wall 140 and the inclined portion 21a and the extending portion 21b of the mounting member 21.
  • the upstream communication passage 120 includes a first communication section 121 and a second communication section 123.
  • the first communication portion 121 is formed between the inclined portion 21a and the inclined portion 141.
  • the first communication portion 121 extends radially inward.
  • the first communication portion 121 extends along the inclined direction of the inclined portions 21a and 141.
  • the second communication unit 123 communicates with the first communication unit 121.
  • the second communication portion 123 is located radially inside the first communication portion 121.
  • the second communication portion 123 is formed between the large diameter portion 143 and the extending portion 21b.
  • the second communication portion 123 extends in the direction of the rotation axis.
  • the present invention is not limited to this, and the second communication portion 123 may be oriented in a direction different from the rotation axis direction.
  • the second communication portion 123 extends in a direction (downstream side) close to the compressor impeller 19.
  • the second communication portion 123 may extend radially inward toward the downstream side.
  • the second communication portion 123 may extend so as to be inclined outward in the radial direction toward the downstream side.
  • the second communication portion 123 may extend in parallel with the direction of the rotation axis.
  • the first communication portion 121 has a substantially constant first flow path cross section. However, the size of the first flow path cross-sectional area of the first communication portion 121 may change in the direction in which the fluid flows. In that case, the smallest flow path cross section of the first communication portion 121 is set as the first flow path cross section.
  • the second communication portion 123 has a substantially constant second flow path cross section. However, the size of the second flow path cross-sectional area of the second communication portion 123 may change in the direction in which the fluid flows. In that case, the smallest flow path cross section of the second communication portion 123 is set as the second flow path cross section. The second flow path cross section is smaller than the first flow path cross section.
  • the downstream continuous passage 130 has a substantially constant third flow path cross section.
  • the size of the third flow path cross-sectional area of the downstream communication passage 130 may change in the direction in which the fluid flows. In that case, the smallest flow path cross section of the downstream continuous passage 130 is set as the third flow path cross section.
  • the cross-sectional area of the second flow path of the second communication portion 123 is smaller than the cross-sectional area of the third flow path of the downstream communication passage 130.
  • the upstream continuous passage 120 includes an outer diameter side opening P1 and an inner diameter side opening P2.
  • the outer diameter side opening P1 opens in the sub-flow path 110.
  • the outer diameter side opening P1 connects the sub-flow passage 110 and the upstream continuous passage 120.
  • the inner diameter side opening P2 opens in the main flow path 23.
  • the inner diameter side opening P2 is formed between the end surface 21c of the extending portion 21b and the large diameter portion 143 of the partition wall 140.
  • the inner diameter side opening P2 connects the upstream continuous passage 120 and the main flow path 23.
  • the inner diameter side opening P2 and the end face 21c are oriented in the rotation axis direction.
  • the present invention is not limited to this, and the inner diameter side opening P2 and the end face 21c may face in a direction different from the rotation axis direction.
  • the inner diameter side opening P2 and the end face 21c are oriented in a direction different from the radial direction.
  • the inner diameter side opening P2 and the end face 21c face in a direction close to the compressor impeller 19 (toward the downstream side).
  • the inner diameter side opening P2 and the end surface 21c are oriented in a direction different from the direction orthogonal to the rotation center axis of the compressor impeller 19.
  • the inner diameter side opening P2 and the end surface 21c may be oriented in a direction inclined inward in the radial direction with respect to the rotation axis direction toward the compressor impeller 19.
  • the inner diameter side opening P2 and the end surface 21c may be oriented in a direction inclined outward in the radial direction with respect to the rotation axis direction toward the compressor impeller 19.
  • the inner diameter side opening P2 and the end face 21c may face in the direction of the rotation axis toward the compressor impeller 19.
  • the inner diameter side opening P2 and the end surface 21c face the partition wall 140 in the rotation axis direction, not facing the leading edge LE of the compressor impeller 19. That is, the inner diameter side opening P2 and the end surface 21c are located radially outside the leading edge LE of the compressor impeller 19. Further, the inner diameter side opening P2 and the end surface 21c face the gradually decreasing portion 145 of the partition wall 140 in the rotation axis direction.
  • the centrifugal compressor C of the present embodiment includes the circulation flow path 100.
  • the flow rate of the fluid (air) passing through the compressor impeller 19 is smaller than the predetermined flow rate, the fluid compressed by the compressor impeller 19 flows backward.
  • the circulation flow path 100 since the circulation flow path 100 is formed, the backflow fluid flows into the sub-flow path 110 through the downstream communication passage 130 and flows out to the main flow path 23 through the upstream communication passage 120. .. In this way, the flow rate of the apparent fluid flowing through the main flow path 23 increases, so that the operating region on the small flow rate side of the centrifugal compressor C expands.
  • the upstream passage 120 of the present embodiment has an inner diameter side opening P2 and an end face 21c facing in a direction (downstream side) close to the compressor impeller 19.
  • the fluid flowing in the main flow path 23 flows toward the compressor impeller 19 along the rotation axis direction.
  • the inner diameter side opening P2 and the end face 21c are oriented in the radial direction, the fluid flowing out from the upstream communication passage 120 to the main flow path 23 pushes out the fluid flowing in the main flow path 23 in the radial direction.
  • the substantially outer diameter of the main flow path 23 is narrowed down, which may be a factor of lowering the compressor efficiency.
  • the inner diameter side opening P2 and the end surface 21c flow out from the upstream communication passage 120 and are directed to the main flow path 23 as compared with the case where the inner diameter side opening P2 and the end surface 21c are oriented in the radial direction.
  • the force of the fluid that pushes the fluid flowing inside in the radial direction weakens.
  • the inner diameter side opening P2 and the end face 21c are oriented in the direction of the rotation axis.
  • the force of the fluid that flows out from the upstream communication passage 120 and pushes out the fluid flowing in the main flow path 23 in the radial direction is exerted. It can be made smaller. As a result, the substantial decrease in the outer diameter of the main flow path 23 can be reduced, and the decrease in the compressor efficiency can be further suppressed.
  • the cross-sectional area of the second flow path of the second communication portion 123 of the upstream communication passage 120 is smaller than the cross-sectional area of the third flow path of the downstream communication passage 130. Therefore, the second communication portion 123 can increase the flow velocity of the fluid flowing through the second communication portion 123 as compared with the case where the cross section of the second flow path is equal to the cross section of the third flow path. As a result, the interference region in which the fluid flowing out from the upstream communication passage 120 interferes with the fluid flowing in the main flow path 23 can be reduced. The smaller the interference region, the smaller the decrease in the substantial outer diameter of the main flow path 23. As a result, the decrease in compressor efficiency can be further suppressed.
  • the second communication portion 123 extends in a direction close to the compressor impeller 19.
  • the inner diameter side opening P2 is closer to the compressor impeller 19 than when the second communication portion 123 does not extend in the direction close to the compressor impeller 19. Become. Therefore, it is possible to reduce the interference region where the fluid flowing out from the upstream continuous passage 120 interferes with the fluid flowing through the main flow path 23.
  • the smaller the interference region the smaller the decrease in the substantial outer diameter of the main flow path 23. As a result, the decrease in compressor efficiency can be further suppressed.
  • the inner diameter side opening P2 and the end surface 21c are located radially outside the leading edge LE of the compressor impeller 19.
  • the substantially outer diameter of the main flow path 23 is narrowed down by the mounting member 21 to be smaller than the outer diameter of the leading edge LE. If the substantial outer diameter of the main flow path 23 flowing into the compressor impeller 19 becomes smaller than the outer diameter of the leading edge LE, it causes a decrease in compressor efficiency.
  • the actual outer diameter of the main flow path 23 becomes equal to or greater than the outer diameter of the leading edge LE, and the compressor efficiency is reduced. It can be suppressed.
  • the inner diameter side opening P2 and the end surface 21c face the gradually decreasing portion 145 of the partition wall 140 in the rotation axis direction.
  • the inner diameter side opening P2 faces the plane portion orthogonal to the rotation center axis of the compressor impeller 19 in the rotation axis direction
  • the fluid flowing out from the inner diameter side opening P2 collides with the plane portion approximately vertically.
  • the interference region that interferes with the fluid flowing out from the inner diameter side opening P2 and the fluid flowing through the main flow path 23 is larger than the case where the inner diameter side opening P2 faces the gradually decreasing portion 145 in the rotation axis direction.
  • the fluid flowing out of the inner diameter side opening P2 and the fluid flowing through the main flow path 23 are more likely to face each other than when the inner diameter side opening P2 faces the flat surface portion.
  • the interference region can be reduced, and a decrease in compressor efficiency can be suppressed.
  • the present invention is not limited to this, and the second channel cross section may be larger than the first channel cross section or may be equal to the first channel cross section. Further, in the above embodiment, an example in which the cross-sectional area of the second flow path of the second communication portion 123 is smaller than the cross-sectional area of the third flow path of the downstream communication passage 130 has been described. However, the cross section of the second channel may be larger than the cross section of the third channel or equal to the cross section of the third channel.

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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

La présente invention concerne un compresseur centrifuge C qui comprend : un chemin d'écoulement principal 23 dans lequel est agencée une roue de compresseur 19 ; un chemin d'écoulement auxiliaire 110 formé plus loin vers l'extérieur dans la direction radiale de la roue de compresseur 19 que le chemin d'écoulement principal 23 ; un passage de communication aval 130 qui est agencé de façon à faire face à la roue de compresseur 19 dans la direction radiale et qui relie le chemin d'écoulement principal 23 et le chemin d'écoulement auxiliaire 110 ; et un passage de communication amont 120 qui est installé plus loin de la roue de compresseur 19 que le passage de communication aval 130 et qui relie le chemin d'écoulement principal 23 et le chemin d'écoulement auxiliaire 110, le passage de communication amont 120 comprenant une partie ouverture PP reliée au chemin d'écoulement principal 23, et une surface d'extrémité 21c de la partie ouverture PP étant tournée vers la roue de compresseur 19.
PCT/JP2021/038265 2020-11-17 2021-10-15 Compresseur centrifuge et compresseur de suralimentation WO2022107519A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2020190970 2020-11-17
JP2020-190970 2020-11-17

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WO2022107519A1 true WO2022107519A1 (fr) 2022-05-27

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Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US7775759B2 (en) * 2003-12-24 2010-08-17 Honeywell International Inc. Centrifugal compressor with surge control, and associated method
US20110255952A1 (en) * 2010-04-19 2011-10-20 GM Global Technology Operations LLC Compressor gas flow deflector and compressor incorporating the same
WO2015001644A1 (fr) * 2013-07-04 2015-01-08 三菱重工業株式会社 Compresseur centrifuge
JP2018173040A (ja) * 2017-03-31 2018-11-08 三菱重工エンジン＆ターボチャージャ株式会社 遠心圧縮機

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US7775759B2 (en) * 2003-12-24 2010-08-17 Honeywell International Inc. Centrifugal compressor with surge control, and associated method
US20110255952A1 (en) * 2010-04-19 2011-10-20 GM Global Technology Operations LLC Compressor gas flow deflector and compressor incorporating the same
WO2015001644A1 (fr) * 2013-07-04 2015-01-08 三菱重工業株式会社 Compresseur centrifuge
JP2018173040A (ja) * 2017-03-31 2018-11-08 三菱重工エンジン＆ターボチャージャ株式会社 遠心圧縮機

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