WO2020170487A1 - 多段遠心流体機械 - Google Patents

多段遠心流体機械 Download PDF

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Publication number
WO2020170487A1
WO2020170487A1 PCT/JP2019/036099 JP2019036099W WO2020170487A1 WO 2020170487 A1 WO2020170487 A1 WO 2020170487A1 JP 2019036099 W JP2019036099 W JP 2019036099W WO 2020170487 A1 WO2020170487 A1 WO 2020170487A1
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WO
WIPO (PCT)
Prior art keywords
return
return bend
bend
flow passage
fluid machine
Prior art date
Application number
PCT/JP2019/036099
Other languages
English (en)
French (fr)
Japanese (ja)
Inventor
澄賢 平舘
小林　博美
西岡　卓宏
Original Assignee
株式会社日立インダストリアルプロダクツ
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 株式会社日立インダストリアルプロダクツ filed Critical 株式会社日立インダストリアルプロダクツ
Priority to KR1020217024031A priority Critical patent/KR102582061B1/ko
Publication of WO2020170487A1 publication Critical patent/WO2020170487A1/ja

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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
    • F04D1/00—Radial-flow pumps, e.g. centrifugal pumps; Helico-centrifugal pumps
    • F04D1/06—Multi-stage pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D17/00—Radial-flow pumps, e.g. centrifugal pumps; Helico-centrifugal pumps
    • F04D17/08—Centrifugal pumps
    • F04D17/10—Centrifugal pumps for compressing or evacuating
    • F04D17/12—Multi-stage pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/18—Rotors
    • F04D29/22—Rotors specially for centrifugal 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
    • F04D29/18—Rotors
    • F04D29/22—Rotors specially for centrifugal pumps
    • F04D29/24—Vanes
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • 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
    • F04D29/26—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
    • F04D29/30—Vanes
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • 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
    • 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
    • F04D29/40—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
    • F04D29/445—Fluid-guiding means, e.g. diffusers especially adapted for liquid pumps
    • 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
    • F05D2210/00—Working fluids
    • F05D2210/10—Kind or type
    • F05D2210/11—Kind or type liquid, i.e. incompressible
    • 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
    • F05D2210/00—Working fluids
    • F05D2210/10—Kind or type
    • F05D2210/12—Kind or type gaseous, i.e. compressible
    • 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
    • F05D2240/20—Rotors

Definitions

  • the present invention relates to a multi-stage centrifugal fluid machine, and more particularly, to a curved flow path (return bend) for diverting a fluid from a radially outward direction to a inward direction, and a swirling component of the fluid in the same direction as the rotation direction of an impeller (
  • the present invention relates to a multi-stage centrifugal fluid machine suitable for use with a circular blade row element (return vane) arranged axially in the circumferential direction to remove (pre-swirl).
  • a multi-stage centrifugal fluid machine in which a plurality of centrifugal impellers are mounted on one rotating shaft, the fluid whose pressure has been increased by each stage impeller is swirled and discharged radially outward, so that on the downstream side in the rotating shaft direction,
  • a curved flow path for diverting the fluid from the radially outward direction to the inward direction is provided.
  • the fluid is arranged axially symmetrically.
  • Circular cascade elements return vanes
  • the return bend the flow is diverted from outward to inward in the radial direction with as little pressure loss as possible, and the working fluid flows into the return vane so that the return vane can sufficiently remove the pre-swirl. Is required to be properly controlled.
  • the return bend and the return channel are collectively referred to as a return flow path.
  • Patent Document 1 describes a conventional example in which the pressure loss in the return passage of the multistage centrifugal fluid machine is reduced.
  • the radius of curvature of the wall surface on the downstream side (the second bend portion of the return bend) is made larger than the radius of curvature of the wall surface on the upstream side (the first bend portion of the return bend) in the flow passage wall surface on the radial inside of the return bend.
  • the front edge of the return vane is configured to be located at the second bend portion of the return bend.
  • the flow passage cross-sectional area at the end of the return bend outlet is the same as the flow passage cross-sectional area at the end of the return bend inlet (end of the diffuser outlet), or It is configured to be large.
  • the uniformity of the flow velocity of the fluid is improved, the separation of the fluid in the return flow path is suppressed, and the pressure loss of the centrifugal fluid machine is reduced.
  • the structure of the return bend and the return vane described in Patent Document 1 aims to reduce the flow velocity Cm of the fluid at the return vane inlet by setting the area of the return vane inlet as large as possible.
  • the inflow angle ⁇ of the fluid to the return vane 8 tends to be smaller than that of the velocity triangle at the leading edge 12 of the return vane shown in FIG. 6, and the vector indicating the direction of the absolute flow velocity C tends to be more circumferential. Show a trend.
  • the inlet angle ⁇ b 5 of the return vane 8 is often designed according to the inflow angle ⁇ of the fluid into the return vane 8.
  • the return vane 8 The entrance angle ⁇ b 5 of is small.
  • the return vane trailing edge 8TE is generally designed so as to face the rotation axis direction in order to eliminate swirling of the fluid.
  • the present invention has been made in view of the above points, and an object thereof is to suppress the occurrence of fluid separation in the return vane and increase the pressure loss even when the length of the return vane cannot be sufficiently secured.
  • (EN) Provided is a multi-stage centrifugal fluid machine capable of suppressing the above and sufficiently removing swirling components of a fluid.
  • the multistage centrifugal fluid machine of the present invention is provided with a plurality of impellers, rotating shafts to which the plurality of impellers are respectively attached, and radially outside of the impellers.
  • a diffuser a return passage provided downstream of the diffuser and for guiding a fluid from the diffuser to the impeller at a subsequent stage, and a plurality of sheets provided in the return passage and arranged at intervals along the circumferential direction.
  • the return flow path has a return bend that guides the fluid sent radially outward from the impeller toward the inner side in the radial direction, and the return bend is the return bend of the return bend.
  • a return bend first bending portion located on the upstream side and a return bend second bending portion located on the downstream side of the return bend first bending portion, and a front edge of the return vane is an outlet of the return bend.
  • a radius of curvature of a wall surface on the radially inner side of the return bend second curved portion which is installed immediately downstream of the return bend first curved portion is larger than a radius of curvature of a wall on the radially inner side of the return bend first curved portion.
  • the flow channel cross-sectional area or flow channel width at the exit of the return bend is set to be equal to or less than the flow channel cross-sectional area or flow channel width at the return bend inlet.
  • the present invention even when the length of the return vane cannot be sufficiently secured, the occurrence of fluid separation in the return vane is suppressed, the increase in pressure loss is suppressed, and the swirling component of the fluid is sufficiently removed. It becomes possible to do.
  • the multistage centrifugal fluid machine of the present invention will be described below based on the illustrated embodiment.
  • the same reference numerals are used for the same components.
  • FIG. 1 is a meridional sectional view showing a part of a conventional multistage centrifugal fluid machine 20
  • FIG. 2 is an entire meridional sectional view of the conventional multistage centrifugal fluid machine 20 including the part shown in FIG. 1 is an example of a single-shaft multi-stage centrifugal compressor.
  • a multistage centrifugal fluid machine 20 includes a centrifugal impeller 1 that imparts rotational energy to a fluid, a rotating shaft 4 to which the centrifugal impeller 1 is attached, and a radial outer side of the centrifugal impeller 1. And a diffuser 5 for converting the dynamic pressure of the fluid discharged from the centrifugal impeller 1 into static pressure. Further, downstream of the diffuser 5, a return flow passage 6 for guiding the fluid to the centrifugal impeller 1 in the subsequent stage is provided downstream of the diffuser 5, a return flow passage 6 for guiding the fluid to the centrifugal impeller 1 in the subsequent stage is provided.
  • the centrifugal impeller 1 is located between the disc (hub) 2 fastened to the rotating shaft 4, the side plate (shroud) 3 facing the hub 2, and the hub 2 and the shroud 3 in the circumferential direction (see FIG. 1). It has a plurality of blades 1A arranged at intervals in the direction perpendicular to the plane of the drawing.
  • FIG. 1 shows the case of a closed type impeller having the shroud 3
  • an open type impeller without the shroud 3 may be used.
  • the diffuser 5 either a vaned diffuser having a plurality of blades arranged at a substantially equal pitch in the circumferential direction or a vaneless diffuser having no blade, which is not shown in FIG. 1, is used. ..
  • the return flow path 6 is composed of a return bend 7 and a return vane 8.
  • the return bend 7 diverts the fluid passing through the diffuser 5 from the radially outward direction to the inward direction, and further, the return vane 8 causes the fluid to flow. It has a role of removing the swirling component of the fluid and rectifying the fluid to flow into the centrifugal impeller 1 of the next stage.
  • the return bend 7 is formed as a U-shaped curved flow path surrounded by surrounding structures in the meridian plane, and the return bend inlet 9 is defined by a substantially cylindrical surface corresponding to the outlet of the diffuser 5.
  • the return bend outlet 10 is defined as a section from the return bend inlet 9 defined by a substantially cylindrical surface corresponding to the end of the meridional curved flow path located immediately upstream of the return vane leading edge 12 to the return bend outlet 10.
  • the return vane 8 is composed of a plurality of blades arranged around the rotating shaft 4 at substantially equal pitches in the circumferential direction.
  • FIG. 2 shows a multistage centrifugal fluid machine 20 in which a plurality of compression stages shown in FIG. 1 are laminated in the axial direction.
  • radial bearings 17 that rotatably support the rotating shaft 4 are arranged at both ends of the rotating shaft 4, and one end of the rotating shaft 4 supports the rotating shaft 4 in the axial direction.
  • a thrust bearing 18 is arranged.
  • centrifugal impeller (five centrifugal impellers in FIG. 2) of multiple compression stages is fixedly attached to the rotary shaft 4, and the downstream side of each centrifugal impeller 1 is shown in FIG. Similarly, the diffuser 5 and the return flow path 6 are provided.
  • the centrifugal impeller 1, the diffuser 5, and the return passage 6 are housed in a casing 19.
  • a suction passage 15 is provided on the suction side of the casing 19, and a discharge passage 16 is provided on the discharge side of the casing 19.
  • the fluid sucked from the suction passage 15 is boosted every time it passes through the centrifugal impeller 1, the diffuser 5 and the return passage 6 at each stage, and finally Then, a predetermined pressure is reached and the liquid is discharged from the discharge channel 16.
  • FIG. 3 is a meridional cross-sectional view showing the vicinity of the return bend 7 in the multistage centrifugal fluid machine 20 of this embodiment.
  • the return flow path 6 has a return bend 7 that guides the fluid, which is sent out from the centrifugal impeller 1 to the outside in the radial direction, toward the inside in the radial direction.
  • the return bend 7 is a return bend. 7
  • the return bend first bending portion 13 is located on the upstream side
  • the return bend second bending portion 14 is located on the downstream side of the return bend first bending portion 13.
  • the return vane front edge 12 mounted downstream of the return bend 7 shown in FIG. 3 is installed immediately downstream of the return bend outlet 10, and in the flow passage wall surfaces 13A, 14A on the radially inner side of the return bend 7,
  • the radius of curvature ⁇ 2 of the flow path wall surface 14A on the radially inner side of the return bend 7 of the return bend second curved portion 14 is the curvature radius ⁇ 1 of the flow path wall surface 13A on the radially inner side of the return bend 7 of the return bend first curved portion 13.
  • the flow passage cross-sectional area at the return bend outlet 10 is set to be equal to or smaller than the flow passage cross-sectional area at the return bend inlet 9.
  • FIG. 4 shows the inlet velocity triangle of the return vane 8 and the streamline of the return vane 8 when this embodiment is applied.
  • the inlet angle ⁇ b 5 of the return vane 8 which is set by matching the inflow angle ⁇ of the fluid into the return vane 8 can be increased. Further, when the return vane trailing edge 8TE is set to face the direction of the rotating shaft 4 in order to remove the swirling of the fluid, the return vane leading edge 12 to the return vane trailing edge 8TE are set in accordance with the contents described above. The deflection of the fluid can be reduced.
  • the flow passage cross-sectional area of the return bend outlet 10 is small, the flow velocity of the fluid in the return bend second curved portion 14 increases, but the flow passage wall surface 14A of the return bend 7 in the radial direction in this region is formed.
  • the radius of curvature ⁇ 2 large, flow separation is suppressed, so that the uniformity of the inflow flow to the leading edge 12 of the return vane is ensured, the pressure loss is reduced, and the return vane 8 is The swirling component of the fluid is sufficiently removed.
  • the length of the return vane 8 is short, and the return vane 8 having a large blade angle difference between the return vane leading edge 12 and the return vane trailing edge 8TE has a short section. Therefore, the fluid has to be largely diverted, and the separation of the flow on the return vane negative pressure surface 8S is more likely to occur.
  • the flow path cross-sectional area in the return bend intermediate portion 11 located between the return bend first bending portion 13 and the return bend second bending portion 14 shown in FIG. 3 is the same as the position of the return bend 7 shown in FIG. (Bend inlet 9, return bend middle portion 11, return bend outlet 10 positions)
  • the flow passage cross-sectional area at the return bend inlet 9 and below, and the flow passage at the return bend outlet 10 It may be set to be equal to or larger than the cross-sectional area (solid line in FIG. 5), or may be set to be equal to or smaller than any cross-sectional area of the flow path at the return bend inlet 9 or the return bend outlet 10 (dotted line in FIG. 5).
  • the return bend inlet 9, that is, the outlet diameter of the diffuser 5 can be set larger. ..
  • the length of the return vane 8 can be increased by increasing the outlet diameter of the diffuser 5, and the amount of static pressure recovery in the diffuser 5 is increased to increase the return.
  • the flow velocity at the bend inlet 9 can be reduced.
  • the radial length of the diffuser 5 When reducing the diameter of the return passage 6, the radial length of the diffuser 5 must be shortened, and the flow velocity at the return bend inlet 9 tends to increase. However, the passage shown by the dotted line in FIG. By setting the cross-sectional area, it is possible to reduce the flow velocity at the return bend inlet 9 while keeping the outermost radius Rtop of the return bend 7 the same when the diameter is reduced.
  • the flow passage cross-sectional area is set to be small at the return bend outlet 10 on the upstream side of the return vane front edge 12, the meridional direction flow velocity Cm at the return vane front edge 12 increases.
  • the inflow angle ⁇ of the fluid into the return vane 8 becomes large. Therefore, the inlet angle ⁇ b 5 of the return vane 8 can be set large, and the turning of the fluid from the return vane inlet 9 to the return vane outlet 10 can be reduced.
  • the flow velocity of the fluid in the return bend second bending portion 14 is increased by setting the flow passage cross-sectional area of the return bend outlet 10 to be small.
  • the curvature radius of the flow path wall surface 14A large, separation of the fluid flow is suppressed, the uniformity of the inflow flow to the return vane leading edge 12 is ensured, and the pressure loss is reduced.
  • the return vane 8 can sufficiently remove the swirling component of the fluid.
  • the return vane leading edge 12 mounted downstream of the return bend 7 is directly downstream of the return bend outlet 10.
  • the radius of curvature ⁇ 2 is made larger than the radius of curvature ⁇ 1 in the flow passage wall surfaces 13A and 14A on the radially inner side of the return bend 7, and the flow passage width be at the return bend outlet 10 is set to the return bend inlet 9 It may be set to be equal to or smaller than the flow path width bs in the above.
  • the flow passage width bm in the return bend intermediate portion 11 may be set to be equal to or smaller than the flow passage width bs at the return bend inlet 9 and equal to or larger than the flow passage width be at the return bend outlet 10.
  • the flow passage widths bs and be at the bend inlet 9 and the return bend outlet 10 may be set to be equal to or less than the widths.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
PCT/JP2019/036099 2019-02-20 2019-09-13 多段遠心流体機械 WO2020170487A1 (ja)

Priority Applications (1)

Application Number Priority Date Filing Date Title
KR1020217024031A KR102582061B1 (ko) 2019-02-20 2019-09-13 다단 원심 유체 기계

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2019-028185 2019-02-20
JP2019028185A JP7272815B2 (ja) 2019-02-20 2019-02-20 多段遠心流体機械

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JP2023001450A (ja) * 2021-06-21 2023-01-06 株式会社日立インダストリアルプロダクツ 多段遠心流体機械

Citations (1)

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Publication number Priority date Publication date Assignee Title
WO2014115417A1 (ja) * 2013-01-28 2014-07-31 三菱重工業株式会社 遠心回転機械

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JPS60141838A (ja) * 1983-12-29 1985-07-26 Showa Alum Corp アルミニウム溶湯処理槽における回転軸挿入口のシ−ル装置
JPS6140736U (ja) 1984-08-20 1986-03-14 パイオニア株式会社 オ−デイオ機器の操作ボタンの機能表示装置
JPH08200289A (ja) * 1995-01-31 1996-08-06 Mitsubishi Heavy Ind Ltd 多段遠心圧縮機
JP2010216456A (ja) 2009-03-19 2010-09-30 Hitachi Plant Technologies Ltd 多段遠心圧縮機及び多段遠心圧縮機の改造方法
DE102009019061A1 (de) 2009-04-27 2010-10-28 Man Diesel & Turbo Se Mehrstufiger Radialverdichter

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Publication number Priority date Publication date Assignee Title
WO2014115417A1 (ja) * 2013-01-28 2014-07-31 三菱重工業株式会社 遠心回転機械

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JP2023058646A (ja) 2023-04-25
JP2020133502A (ja) 2020-08-31
JP7429810B2 (ja) 2024-02-08
JP7272815B2 (ja) 2023-05-12
KR20210128386A (ko) 2021-10-26
KR102582061B1 (ko) 2023-09-22

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