WO2016158636A1 - ディフューザを備える流体機械 - Google Patents

ディフューザを備える流体機械 Download PDF

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Publication number
WO2016158636A1
WO2016158636A1 PCT/JP2016/059302 JP2016059302W WO2016158636A1 WO 2016158636 A1 WO2016158636 A1 WO 2016158636A1 JP 2016059302 W JP2016059302 W JP 2016059302W WO 2016158636 A1 WO2016158636 A1 WO 2016158636A1
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WO
WIPO (PCT)
Prior art keywords
diffuser
channel
flow path
fluid
fluid machine
Prior art date
Application number
PCT/JP2016/059302
Other languages
English (en)
French (fr)
Japanese (ja)
Inventor
夕美子 関野
啓悦 渡邉
ファイドン クリスタコポロス
メーダッド ザンゲネ
Original Assignee
株式会社荏原製作所
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 株式会社荏原製作所 filed Critical 株式会社荏原製作所
Priority to JP2017509854A priority Critical patent/JP6706248B2/ja
Priority to US15/563,361 priority patent/US20180080471A1/en
Priority to CN201680021211.0A priority patent/CN107949705B/zh
Priority to EP16772517.5A priority patent/EP3279479A4/en
Publication of WO2016158636A1 publication Critical patent/WO2016158636A1/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
    • 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
    • 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
    • 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
    • F04D29/40—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
    • F04D29/448—Fluid-guiding means, e.g. diffusers especially adapted for liquid pumps bladed 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
    • F04D29/04—Shafts or bearings, or assemblies thereof
    • F04D29/043—Shafts
    • 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

Definitions

  • the present invention relates to a fluid machine including a diffuser.
  • a diffuser pump that transports water is known as a fluid machine including a diffuser.
  • a diffuser pump can transfer water at high pressure by applying kinetic energy to water with a rotating impeller and converting it into pressure energy with a diffuser provided on the discharge side of the impeller.
  • a high-pressure multi-stage diffuser pump includes a plurality of impellers fixed to a rotating shaft.
  • a diffuser is provided on the radially outer side of each stage of the impeller.
  • the diffuser is formed with diffuser blades that define a plurality of diffuser flow paths configured to allow fluid discharged from the impeller to pass through. The fluid that has passed through the diffuser flow path is guided to the next stage impeller.
  • a diffuser pump In the diffuser pump, the diffuser is designed to reduce the pressure loss of the fluid passing through the pump, make the flow uniform, and improve the pump efficiency.
  • various shapes of the diffuser channel Conventionally, in order to improve the pump efficiency of the diffuser pump, various shapes of the diffuser channel have been studied (Patent Document 1).
  • a diffuser pump generally includes a plurality of diffuser channels, but all conventional diffuser channels have the same shape.
  • the diffuser flow paths are all designed to have the same shape. However, depending on the shape of the flow path downstream from the diffuser, the flow of fluid discharged from the diffuser may not always be uniform. If the flow of fluid discharged from the diffuser enters the next stage impeller without being properly rectified, the pump efficiency may decrease.
  • a fluid machine having a diffuser for converting the kinetic energy of the fluid into pressure energy.
  • the diffuser has a first diffuser flow path and a second diffuser flow path configured to allow fluid to pass through, and the shapes of the first diffuser flow path and the second diffuser flow path are different.
  • each of the first diffuser channel and the second diffuser channel has an inlet of the diffuser channel, and at least one of the first diffuser channel and the second diffuser channel.
  • the cross-sectional areas of the first diffuser flow path and the second diffuser flow path that are orthogonal to the flow path center at the same distance from the inlet of each diffuser flow path are different from each other.
  • the fluid machine in a fluid machine, includes a first impeller that rotationally drives and imparts kinetic energy to the fluid, and the first diffuser channel and the second diffuser channel Located downstream of the first impeller in the flow direction.
  • the first diffuser channel and the second diffuser channel each have an outlet of the diffuser channel
  • the fluid machine includes the first diffuser channel and the second diffuser flow.
  • a first return channel fluidly coupled to the first merge channel, and the first return channel extends in the direction of the rotation axis of the first impeller.
  • the second diffuser channel is located closer to the first return channel than the first diffuser channel, and the cross-sectional area of the second diffuser channel is the first It is larger than the cross-sectional area of the diffuser channel.
  • the first diffuser channel and the second diffuser channel have a cross-sectional area that increases from an inlet of each diffuser channel toward an outlet of the diffuser channel.
  • the second diffuser flow path has a region in which the rate of increase in cross-sectional area is relatively large, a small region, and a large region in order from the diffuser flow channel inlet to the diffuser flow channel outlet.
  • the diffuser in a fluid machine, includes a third diffuser channel and a fourth diffuser channel configured to allow fluid to pass therethrough, and the third diffuser channel and the fourth diffuser channel.
  • the channel is located downstream of the first impeller in the fluid flow direction, the third diffuser channel and the fourth diffuser channel each have an outlet of the diffuser channel, and the fluid machine includes the third diffuser channel A second merging channel fluidly coupled to the outlet of each diffuser channel of the fourth diffuser channel, and a second return fluidly coupled to the second merging channel for supplying fluid to the second impeller.
  • the second return channel extends in the direction of the drive shaft of the first impeller.
  • the third diffuser channel and the fourth diffuser channel have shapes that are rotationally symmetric with respect to the first diffuser channel and the second diffuser channel, respectively.
  • the third diffuser channel and the fourth diffuser channel have a cross-sectional area that increases from an inlet of each diffuser channel toward an outlet of the diffuser channel.
  • the fourth diffuser flow path has a region in which the increase rate of the cross-sectional area is relatively large, a small region, and a large region in order from the inlet of the diffuser flow channel to the outlet of the diffuser flow channel.
  • FIG. 3 is a cross-sectional perspective view taken along the line AA and the rotation axis of FIG.
  • FIG. 3 is a cross-sectional view taken along line AA in FIG.
  • FIG. 6 is a plan view showing a diffuser flow path according to one embodiment. 6 is a graph showing the relative size of the cross-sectional area at each position of each diffuser channel, according to one embodiment.
  • FIG. 6 is a cross-sectional perspective view of a diffuser channel, according to one embodiment.
  • FIG. 8 is a view showing a cross-sectional shape at positions P01 to P06 of the diffuser flow path shown in FIG. It is a graph which shows the relative flow volume of the fluid in each diffuser flow path by one Embodiment and each diffuser flow path by a comparative example. It is a figure which shows the pressure loss of each diffuser flow path and merge flow path by one Embodiment, and each diffuser flow path and merge flow path of a comparative example.
  • FIG. 6 is a diagram showing the flow velocity of fluid at cross-sectional positions P01 to P06 of a diffuser flow path 104-5 according to a comparative example.
  • FIG. 6 is a diagram showing the flow velocity of the fluid at each of the cross-sectional positions P01 to P06 of the diffuser flow path 104-5 according to one embodiment.
  • FIG. 1 is a cross-sectional view illustrating an overall configuration of a multistage diffuser pump 1A according to an embodiment of the present disclosure.
  • the multistage diffuser pump 1 ⁇ / b> A includes a rotating member 30 and a stationary member 40.
  • Rotating member 30 includes a rotating shaft 10 supported at both ends. First to seventh impellers I1 to I7 are attached to the impeller attachment portions 10a to 10g of the rotary shaft 10. The rotating member 30 is mounted so as to be rotatable within the stationary member 40.
  • the stationary member 40 has an outer trunk portion 25.
  • the outer body portion 25 includes a cylindrical member 20 that includes a suction port Wi and a discharge port Wo.
  • the outer body portion 25 includes a suction side plate 18 and a discharge side plate 22 that close both ends of the tubular member 20.
  • the stationary member 40 further has an inner trunk portion 2A. Diffuser blades V1 to V7 that form pumps P1 to P7 of each stage together with the impellers I1 to I7 are formed in the inner trunk portion 2A.
  • the first pump P1 is in the low-pressure chamber R1 communicating with the water inlet Wi, and is composed of an impeller I1 and a diffuser blade V1.
  • the second to seventh pumps P2 to P7 are composed of impellers I2 to I7 and diffuser blades V2 to V7.
  • the seventh pump P7 communicates with the high-pressure chamber R2 that communicates with the discharge port Wo.
  • FIG. 2 is a cross-sectional view of the periphery of the impellers I1 and I2 and the diffuser blades V1 and V2 of the multistage diffuser pump according to the embodiment of the present disclosure.
  • the impellers I ⁇ b> 1 and I ⁇ b> 2 fixed to the rotary shaft 10 include a plurality of impeller blades 50, a hub 52 in which the impeller blades 50 are arranged at equal intervals, and the impeller blades 50.
  • a shroud 54 covering the front surface.
  • a diffuser portion 100 is formed on the downstream side of the impellers I1 and I2, that is, on the radially outer side.
  • FIG. 3 is a cross-sectional perspective view taken along the line AA and the rotation axis of FIG. 4 is a cross-sectional view taken along line AA in FIG. 3 and 4, the impeller I and the rotating shaft 10 are omitted in order to clarify the illustration of the diffuser unit 100.
  • the diffuser unit 100 has a plurality of diffuser blades 102.
  • a diffuser flow path 104 is defined by the wall surface 109 on the hub 52 side, the wall surface 110 on the shroud 54 side, and each diffuser blade 102.
  • the hub 52 and the shroud 54 are a main plate and a side plate of the impeller 102, respectively.
  • each diffuser channel 104 is formed so that its cross-sectional area increases from the inlet 106 of the diffuser channel 104 toward the outlet 108 of the diffuser channel 104. Further, at least some of the diffuser channels 104 have different shapes. In FIG. 3, the arrow indicates the direction of fluid flow.
  • a merging channel 150 that is in fluid communication with the diffuser channel 104 is formed on the downstream side of the outlet 108 of the diffuser channel 104, that is, on the radially outer side.
  • four diffuser channels 104 are in fluid communication with one merge channel 150, and two sets of four diffuser channels 104 and one merge channel 150 are formed.
  • the merge channel 150 is in the same plane as the diffuser channel 104.
  • the number of the diffuser flow path 104 and the merge flow path 150 is arbitrary. For example, in another embodiment, three diffuser channels may be in fluid communication with one merge channel, and three sets of them may be formed.
  • the fluid discharged by applying kinetic energy by the impeller I1 enters the diffuser flow path 104 and is converted into pressure energy.
  • the fluid exiting from the outlet 108 of the diffuser channel 104 of each diffuser channel 104 enters a merging channel 150 formed downstream of the outlet 108 of the diffuser channel 104.
  • the plurality of diffuser flow paths 104 are shaped in consideration of the shape of the downstream merge flow path 150 so that the fluid discharged from the diffuser flow path 104 is not lost as much as possible. Designed.
  • a return channel 200 that is in fluid communication with the merge channel 150 is formed downstream of the merge channel 150.
  • the return channel 200 extends in the direction of the rotating shaft 10 as a whole.
  • a return channel 250 that is in fluid communication with the return channel 200 is formed downstream of the return channel 200.
  • the return flow path 250 as a whole extends radially inward toward the rotary shaft 10. Downstream of the return flow path 250, the next stage impeller I2 is formed.
  • the fluid exiting the impeller I1 passes through the diffuser flow path 104, and then is supplied to the next stage impeller I2 through the merging flow path 150, the return flow path 200, and the return flow path 250. Is done.
  • each diffuser channel 104 is formed so that its cross-sectional area increases from the inlet 106 of the diffuser channel 104 toward the outlet 108 of the diffuser channel 104. Further, at least some of the diffuser channels 104 have different shapes. Hereinafter, the shape of the diffuser flow path 104 in one embodiment will be described in detail.
  • FIG. 4 is a plan view showing the diffuser flow path 104 and the merge flow path 150 cut out along the line AA in FIG.
  • eight diffuser channels 104 are defined between the eight diffuser vanes 102.
  • Diffuser flow paths 104-1, 104-8, 104-7, and 104-6 are in fluid communication with merge flow path 150-1.
  • Diffuser flow paths 104-2, 104-3, 104-4, and 104-5 are in fluid communication with merge flow path 150-2.
  • the diffuser channels 104-1, 104-8, 104-7, and 104-6 are group 1 and the diffuser channels 104-2, 104-3, 104-4, and 104-5 are group 2.
  • the fluid that has passed through the diffuser channels 104 of the group 1 and group 2 is supplied to the impeller at the next stage through the merging channel 150, the return channel 200, and the return channel 250.
  • FIG. 5 is a plan view showing one of the diffuser channels 104 according to one embodiment.
  • a curve connecting the centers of the circles inscribed in the two diffuser blades 102 is defined as the flow path center of the diffuser flow path 104.
  • a cross section perpendicular to the center of the channel on the most upstream side is defined as the inlet 106 of the diffuser channel 104.
  • a cross section perpendicular to the center of the channel on the most downstream side (right side in FIG. 5) is defined as the outlet 108 of the diffuser channel 104.
  • the diffuser channel 104 has a channel cross-sectional area that increases from the inlet 106 of the diffuser channel 104 toward the outlet 108 of the diffuser channel 104.
  • at least a part of the plurality of diffuser channels 104 in the same group is different in shape from the other diffuser channels 104 in the same group. More specifically, the degree of increase in the cross-sectional area of the diffuser flow path 104 is different.
  • the cross-sectional areas of the diffuser channels 104 orthogonal to the channel center at the same distance from the inlet 106 of each diffuser channel 104 are different.
  • the diffuser flow path 104 located near the return flow path 200 that is in fluid communication with the merge flow path 150 can be configured such that the degree of increase in the cross-sectional area of the flow path increases.
  • the return flow path 200 is located near the diffuser flow paths 104-1 and 104-5. Therefore, the diffuser channels 104-1 and 104-5 close to the return channel 200 are more than the other diffuser channels 104-2, 104-3, 104-4, 104-6, 104-7, and 104-8.
  • the degree of increase in the channel cross-sectional area is large.
  • FIG. 6 is a graph showing the relative sizes of the cross-sectional areas at the respective positions of the diffuser channels 104-1 to 104-8 according to one embodiment.
  • the horizontal axis represents the positions P01 to P06 of the diffuser channel shown in FIG.
  • the position P01 corresponds to the inlet 106 of the diffuser channel 104
  • the position P06 corresponds to the outlet 108 of the diffuser channel 104.
  • the vertical axis of the graph in FIG. 6 represents the relative flow path cross-sectional area when the cross-sectional area at the position P01 of one diffuser flow path 104 as a comparative example is 100.
  • the cross-sectional area of the diffuser flow path 104 close to the return flow path 200 is a region where the increase rate of the cross-sectional area is relatively large from the inlet 106 of the diffuser flow path 104 to the outlet 108 of the diffuser flow path 104.
  • Small area large area.
  • the increase rate of the cross-sectional area of the diffuser flow path 104-5 near the return flow path 200 is large from the position P01 to the position P02, and is increased from the position P02 to the position P03. It becomes relatively small, and the increase rate increases again from the position P03 to the position P04.
  • the mixing loss can be reduced when the fluid from the other diffuser flow path 104 is merged in the merge flow path 150.
  • the Group 1 diffuser channels 104-1, 104-8, 104-7, 104-6 and the Group 2 diffuser channels 104-5, 104-4, 104-3, 104-2 are:
  • the shapes may be rotationally symmetric.
  • FIG. 7 and 8 are diagrams showing an example of a cross-sectional shape of the diffuser flow path 104 according to an embodiment.
  • FIG. 7 is a cross-sectional perspective view of the diffuser flow path 104 and schematically shows a cross-sectional shape at positions P01 to P06.
  • the front diffuser blade 102 is indicated by a broken line.
  • FIG. 8 shows cross-sectional shapes at positions P01 to P06 shown in FIG. 7 and 8, the upper side is the wall surface 110 on the shroud 54 side, and the lower side is the wall surface 109 on the hub 52 side.
  • the diffuser flow path 104 is provided with a convex portion in the direction of the rotating shaft 10 to change the size of the cross-sectional area.
  • the diffuser channel 104 is convex on the shroud side at positions P01 and P02, is convex on the hub side at position P03, and is shroud at positions P04 to P06. Convex on both the side and the hub side.
  • the cross-sectional shape in each position of the diffuser flow path 104 is arbitrary, and can be made into a different shape in other embodiments.
  • a convex shape is formed only on the wall surface 110 on the shroud side and a convex shape is formed only on the wall surface 109 on the hub side from the inlet 106 of the diffuser flow path 104 to the outlet 108 of the diffuser flow path 104.
  • both the shroud-side wall surface 110 and the hub-side wall surface 109 can have any shape that is convex.
  • the graph shown in FIG. 9 shows the flow rate per unit time of each diffuser flow path in numerical fluid dynamics (in a pump including a diffuser flow path according to an embodiment of the present invention and a pump including a diffuser flow path according to a comparative example).
  • the results obtained by flow analysis using CFD (Computational Fluids) are shown.
  • the horizontal axis indicates the diffuser channels 104-1 to 104-8 shown in FIG. 4, and the vertical axis indicates the relative flow rate in each of the diffuser channels 104-1 to 104-8. Represents.
  • the relative flow rate is 1, it means that the fluid flows at the same flow rate in all the diffuser flow paths 104-1 to 104-8.
  • the diffuser channels 104-1 to 104-8 are changed by changing the cross-sectional shape for each of the diffuser channels 104-1 to 104-8 as in the embodiment of the present disclosure.
  • the variation in the flow rate is small. That is, in the embodiment of the present disclosure, the mixing loss in the merging channel 150 downstream of the diffuser channel 104 is reduced as compared with the comparative example in which the shapes of the diffuser channels 104 are all the same.
  • FIG. 10 is a diagram illustrating a result of pressure loss in the diffuser flow path 104 and the merge flow path 150 according to the CFD simulation.
  • the magnitude of the pressure loss is shown in gray scale, and the darker the black, the greater the pressure loss.
  • the pressure loss as a whole is smaller in the embodiment of the present disclosure than in the comparative example.
  • FIG. 11 is a diagram showing the flow velocity of the fluid at the respective cross-sectional positions P01 to P06 of the diffuser flow path 104-5 according to the comparative example.
  • FIG. 12 is a diagram illustrating the flow velocity of the fluid at each of the cross-sectional positions P01 to P06 of the diffuser flow path 104-5 according to the embodiment of the present disclosure.
  • the flow velocity at each of the cross-sectional positions P01 to P06 is indicated by an isovelocity line, indicating that the flow velocity is larger toward the center of the cross section.
  • the distortion of the uniform flow velocity line is smaller than that of the comparative example, and the flow velocity distribution has a clean curve. Therefore, in the embodiment of the present disclosure, the fluid flow through the diffuser flow path is uniform, and the rectifying effect is improved. According to the embodiment of the present disclosure, noise and vibration in the pump can be reduced by increasing the pressure loss and rectifying effect.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
PCT/JP2016/059302 2015-03-30 2016-03-24 ディフューザを備える流体機械 WO2016158636A1 (ja)

Priority Applications (4)

Application Number Priority Date Filing Date Title
JP2017509854A JP6706248B2 (ja) 2015-03-30 2016-03-24 ディフューザを備える流体機械
US15/563,361 US20180080471A1 (en) 2015-03-30 2016-03-24 Fluid machine including diffuser
CN201680021211.0A CN107949705B (zh) 2015-03-30 2016-03-24 具有扩散器的流体机械
EP16772517.5A EP3279479A4 (en) 2015-03-30 2016-03-24 Fluid machine equipped with diffuser

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2015068481 2015-03-30
JP2015-068481 2015-03-30

Publications (1)

Publication Number Publication Date
WO2016158636A1 true WO2016158636A1 (ja) 2016-10-06

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PCT/JP2016/059302 WO2016158636A1 (ja) 2015-03-30 2016-03-24 ディフューザを備える流体機械

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US (1) US20180080471A1 (zh)
EP (1) EP3279479A4 (zh)
JP (1) JP6706248B2 (zh)
CN (1) CN107949705B (zh)
WO (1) WO2016158636A1 (zh)

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Publication number Priority date Publication date Assignee Title
JP7469990B2 (ja) 2020-08-07 2024-04-17 日立Astemo株式会社 ２段遠心ポンプ

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ITUB20153032A1 (it) * 2015-08-10 2017-02-10 Nuovo Pignone Tecnologie Srl Pompa centrifuga
US11473589B2 (en) * 2018-05-18 2022-10-18 Franklin Electric Co., Inc. Impeller assemblies and method of making

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JPH11303797A (ja) * 1998-04-20 1999-11-02 Hitachi Ltd 多段圧縮機
JP2010071241A (ja) * 2008-09-19 2010-04-02 Mitsubishi Heavy Ind Ltd 遠心圧縮機

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DE3912279A1 (de) * 1989-04-14 1990-10-18 Klein Schanzlin & Becker Ag Leitrad fuer kreiselpumpen
DE4418662C2 (de) * 1994-05-27 1997-06-05 Grundfos As Kreiselpumpe
JP2002155896A (ja) * 2000-11-22 2002-05-31 Mitsubishi Heavy Ind Ltd ターボ形圧縮機及びそれを備えた冷凍装置
JP4872456B2 (ja) * 2006-05-24 2012-02-08 パナソニック電工株式会社 ポンプ及び液体供給装置
EP2014925A1 (de) * 2007-07-12 2009-01-14 ABB Turbo Systems AG Diffuser für Radialverdichter

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JPH11303797A (ja) * 1998-04-20 1999-11-02 Hitachi Ltd 多段圧縮機
JP2010071241A (ja) * 2008-09-19 2010-04-02 Mitsubishi Heavy Ind Ltd 遠心圧縮機

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Title
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Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP7469990B2 (ja) 2020-08-07 2024-04-17 日立Astemo株式会社 ２段遠心ポンプ

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EP3279479A1 (en) 2018-02-07
CN107949705A (zh) 2018-04-20
JPWO2016158636A1 (ja) 2018-01-25
US20180080471A1 (en) 2018-03-22
JP6706248B2 (ja) 2020-06-03
EP3279479A4 (en) 2018-12-12
CN107949705B (zh) 2020-03-17

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