US20180080471A1 - Fluid machine including diffuser - Google Patents

Fluid machine including diffuser Download PDF

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Publication number
US20180080471A1
US20180080471A1 US15/563,361 US201615563361A US2018080471A1 US 20180080471 A1 US20180080471 A1 US 20180080471A1 US 201615563361 A US201615563361 A US 201615563361A US 2018080471 A1 US2018080471 A1 US 2018080471A1
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United States
Prior art keywords
flow passage
diffuser
diffuser flow
impeller
fluid
Prior art date
Legal status (The legal status 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 status listed.)
Abandoned
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US15/563,361
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English (en)
Inventor
Yumiko SEKINO
Hiroyoshi Watanabe
Faidon CHRISTAKOPOULOS
Mehrdad Zangeneh
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Advanced Design Technology Ltd
Ebara Corp
Original Assignee
Advanced Design Technology Ltd
Ebara Corp
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 Advanced Design Technology Ltd, Ebara Corp filed Critical Advanced Design Technology Ltd
Assigned to EBARA CORPORATION, Advanced Design Technology Ltd. reassignment EBARA CORPORATION ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: SEKINO, Yumiko, WATANABE, HIROYOSHI, ZANGENEH, MEHRDAD
Publication of US20180080471A1 publication Critical patent/US20180080471A1/en
Abandoned legal-status Critical Current

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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.
  • the diffuser pump can give water kinetic energy by an impeller that is rotatable component of a diffuser pump, can convert the kinetic energy into pressure energy by a diffuser provided on a discharge side of the impeller, and can transport the water under high pressure.
  • a high-pressure multi-stage diffuser pump includes a plurality of impellers fixed to a rotatable shaft.
  • a diffuser is mounted outside the impeller of each stage in a radial direction.
  • Diffuser vanes that define a plurality of diffuser flow passages configured such that a fluid discharged from the impellers passes through them are fixed in the diffuser. The fluid having passed through the diffuser flow passages is guided to the impeller of a next stage.
  • the diffuser In the diffuser pump, the diffuser is designed so that a pressure loss of the fluid that passes through the pump is reduced, a flow is made uniform, and that pump efficiency is improved.
  • various shapes of diffuser flow passages have been developed in order to improve pump efficiency of a diffuser pump (Patent Literature 1).
  • a diffuser pump generally includes a plurality of diffuser flow passages, conventional diffuser flow passages all have the same shape.
  • Patent Literature 1 Japanese Patent Laid-Open No. 2013-209883
  • diffuser flow passages are all designed to have the same shape, a flow of a fluid discharged from a diffuser is not always uniform in some cases depending on shapes of flow passages located on a downstream of the diffuser.
  • pump efficiency may be lowered.
  • One object of the present disclosure is to provide each diffuser flow passage for reducing a pressure loss as a whole.
  • one object of the present disclosure is to provide each diffuser flow passage for making uniform a flow on a downstream of a diffuser.
  • a fluid machine having a diffuser for converting kinetic energy of a fluid into pressure energy.
  • the diffuser has first and second diffuser flow passages configured such that the fluid passes through the first and second diffuser flow passages.
  • the first and second diffuser flow passages have different shapes.
  • each of the first and second diffuser flow passages has an inlet.
  • a cross sectional area perpendicular to each of flow passage centers at a position with an equal distance from each of the inlets of the first and second diffuser flow passages is different from each other.
  • the fluid machine has a first rotatable impeller for giving the fluid kinetic energy, and the first and second diffuser flow passages are located on a downstream of the first impeller in a flow direction of the fluid.
  • each of the first and second diffuser flow passages has an outlet.
  • the fluid machine has: a first confluence flow passage fluidly connected to each of the outlets of the first and second diffuser flow passages; a first crossover flow passage fluidly connected to the first confluence flow passage, the first crossover flow passage running in a direction of a rotatable shaft of the first impeller; and a first return flow passage for supplying the fluid to a second impeller of a next stage, the second impeller located on a downstream of the first impeller in a flow direction of the fluid, the first return flow passage being fluidly connected to the first crossover flow passage.
  • the first return flow passage runs in a radially inward direction to a rotatable shaft of the first impeller.
  • the second diffuser flow passage is located closer to the first crossover flow passage than the first diffuser flow passage, and a cross sectional area of the second diffuser flow passage is larger than that of the first diffuser flow passage.
  • the first and second diffuser flow passages are configured such that each of the cross sectional areas are increased from the inlets toward the outlets of the respective diffuser flow passages.
  • the second diffuser flow passage has a relatively large region, small region, and large region in increase rates of the cross sectional areas from the inlet toward the outlet of the diffuser flow passage.
  • the diffuser in the fluid machine, has third and fourth diffuser flow passages configured such that the fluid passes through the third and fourth diffuser flow passages.
  • the third and fourth diffuser flow passages are located on the downstream of the first impeller in the flow direction of the fluid.
  • Each of the third and fourth diffuser flow passages has an outlet.
  • the fluid machine has: a second confluence flow passage fluidly connected to each of the outlets of the third and fourth diffuser flow passages; a second crossover flow passage fluidly connected to the second confluence flow passage, the second crossover flow passage running in a direction of a rotatable shaft of the first impeller; and a second return flow passage for supplying the fluid to the second impeller, the second return flow passage being fluidly connected to the second crossover flow passage.
  • the second return flow passage runs in a radially inward direction to a rotatable shaft of the first impeller.
  • the third and fourth diffuser flow passages have shapes of rotation symmetry of the first and second diffuser flow passages, respectively.
  • the third and fourth diffuser flow passages are configured such that each of the cross sectional areas are increased from inlets toward the outlets of the respective diffuser flow passages.
  • the fourth diffuser flow passage has a relatively large region, small region, and large region in increase rates of the cross sectional areas from the inlet toward the outlet of the diffuser flow passage.
  • FIG. 1 is a cross-sectional view showing an overall configuration of a multi-stage diffuser pump according to one embodiment
  • FIG. 2 is a cross-sectional view of a periphery of impellers and diffuser vanes of a multi-stage diffuser pump according to one embodiment
  • FIG. 3 is a perspective view of a cross section cut out along a line segment A-A and a direction of a rotatable shaft of FIG. 2 ;
  • FIG. 4 is a view of a cross-section cut out along the line segment A-A of FIG. 2 ;
  • FIG. 5 is a plan view showing a diffuser flow passage according to one embodiment
  • FIG. 6 is a graph showing a relative size of a cross-sectional area in each position of each diffuser flow passage according to one embodiment
  • FIG. 7 is a perspective view of a cross section of a diffuser flow passage according to one embodiment
  • FIG. 8 is a view showing cross-sectional shapes in positions P 01 to P 06 of the diffuser flow passage shown in FIG. 7 ;
  • FIG. 9 is a graph showing relative flow rates of a fluid in each diffuser flow passage according to one embodiment and each diffuser flow passage according to a comparative example;
  • FIG. 10 is a view showing pressure losses of each diffuser flow passage and each confluence flow passage according to one embodiment, and of each diffuser flow passage and each confluence flow passage of the comparative example;
  • FIG. 11 is a view showing a flow velocity of a fluid in each of cross-sectional positions P 01 to P 06 of a diffuser flow passage 104 - 5 according to the comparative example.
  • FIG. 12 is a view showing a flow velocity of a fluid in each of the cross-sectional positions P 01 to P 06 of the diffuser flow passage 104 - 5 according to one embodiment.
  • FIG. 1 is a cross-sectional view showing an overall configuration of a multi-stage diffuser pump 1 A according to one embodiment of the present disclosure.
  • the multi-stage diffuser pump 1 A includes a rotatable member 30 and a stationary member 40 .
  • the rotatable member 30 includes a rotatable shaft 10 whose both ends are supported. First to seventh impellers I 1 to 17 are attached to impeller attaching parts 10 a to 10 g of the rotatable shaft 10 .
  • the rotatable member 30 is mounted rotatably in the stationary member 40 .
  • the stationary member 40 has an outer body part 25 .
  • the outer body part 25 has a cylindrical member 20 including a suction opening Wi and a discharge opening Wo.
  • the outer body part 25 has a suction side plate 18 and a discharge side plate 22 that close both ends of the cylindrical member 20 .
  • the stationary member 40 further has an inner body part 2 A. Diffuser vanes V 1 to V 7 that form pumps P 1 to P 7 of each stage along with the impellers I 1 to 17 are formed at the inner body part 2 A.
  • the first pump P 1 is located in a low-pressure chamber R 1 that communicates with the suction opening Wi, and includes the impeller I 1 and the diffuser vane V 1 .
  • the second to seventh pumps P 2 to P 7 include the impellers I 2 to I 7 and the diffuser vanes V 2 to V 7 .
  • the seventh pump P 7 communicates with a high-pressure chamber R 2 that communicates with the discharge port Wo.
  • FIG. 2 is cross-sectional view of a periphery of the impellers Il and 12 , and the diffuser vanes V 1 and V 2 of a multi-stage diffuser pump according to one embodiment of the present disclosure.
  • the impellers I 1 and I 2 fixed to the rotatable shaft 10 each have: a plurality of impeller blades 50 ; a hub 52 at which the impeller blades 50 have been arranged at equal intervals; and a shroud 54 that covers a front surface of the impeller blades 50 .
  • a diffuser part 100 is formed on a downstream side of the impellers I 1 and I 2 , i.e., outside in a radial direction.
  • FIG. 3 is a perspective view of a cross section cut out along a line segment A-A and a direction of the rotatable shaft of FIG. 2 .
  • FIG. 4 is a view of a cross-section cut out along the line segment A-A of FIG. 2 . Note that in FIGS. 3 and 4 , the impeller I and the rotatable shaft 10 are omitted in order to make clear illustration of the diffuser part 100 .
  • the diffuser part 100 has a plurality of diffuser vanes 102 .
  • Diffuser flow passages 104 are defined by a wall surface 109 at a hub 52 side, a wall surface 110 at a shroud 54 side, and each diffuser vane 102 , respectively.
  • each diffuser flow passage 104 is formed so that a cross-sectional area thereof is increased from an inlet 106 toward an outlet 108 of the diffuser flow passage 104 .
  • at least some diffuser flow passages 104 have shapes different from each other. Note that arrows indicate a flow direction of a fluid in FIG. 3 .
  • a confluence flow passage 150 that fluidly communicates with the diffuser flow passage 104 is formed on a downstream side of the outlet 108 of the diffuser flow passage 104 , i.e., outside in the radial direction.
  • the four diffuser flow passages 104 fluidly communicate with the one confluence flow passage 150 , and two sets of the four diffuser flow passages 104 and the one confluence flow passage 150 are formed.
  • the confluence flow passage 150 is located in the same flat surface as the diffuser flow passage 104 .
  • the number of the diffuser flow passages 104 and the confluence flow passages 150 can be arbitrary. For example, in the other embodiment, three diffuser flow passages may fluidly communicate with one confluence flow passage, and three sets of them may be formed.
  • the fluid to which kinetic energy has been given by the impeller Il and that has been discharged enters the diffuser flow passage 104 , and the kinetic energy is converted into pressure energy.
  • the fluid having come out of the outlet 108 of the each diffuser flow passage 104 enters the confluence flow passage 150 formed on a downstream of the outlet 108 of the diffuser flow passage 104 .
  • shapes of the plurality of diffuser flow passages 104 are designed in consideration of a shape of the confluence flow passage 150 located on the downstream so that the pressure loss of the fluid discharged from the diffuser flow passages 104 is minimized.
  • a crossover flow passage 200 that fluidly communicates with the confluence flow passage 150 is formed in a downstream of the confluence flow passage 150 .
  • the crossover flow passage 200 extends in a direction of the rotatable shaft 10 as a whole.
  • a return flow passage 250 that fluidly communicates with the crossover flow passage 200 is formed in a downstream of the crossover flow passage 200 .
  • the return flow passage 250 extends in radially inward direction to the rotatable shaft 10 as a whole.
  • the impeller I 2 of a next stage is formed on a downstream of the return flow passage 250 .
  • the fluid having come out of the impeller I 1 passes through the diffuser flow passages 104 , and is subsequently supplied to the impeller I 2 of the next stage through the confluence flow passage 150 , the crossover flow passage 200 , and the return flow passage 250 .
  • each diffuser flow passage 104 is formed so that the cross-sectional area thereof is increased from the inlet 106 toward the outlet 108 of the diffuser flow passage 104 .
  • at least some diffuser flow passages 104 have the shapes different from each other.
  • the shapes of the diffuser flow passages 104 in one embodiment will be explained in detail.
  • FIG. 4 is a plan view showing the diffuser flow passages 104 and the confluence flow passages 150 cut out along the line segment A-A of FIG. 2 .
  • the eight diffuser flow passages 104 are defined among the eight diffuser vanes 102 .
  • Diffuser flow passages 104 - 1 , 104 - 8 , 104 - 7 , and 104 - 6 fluidly communicate with a confluence flow passage 150 - 1 .
  • Diffuser flow passages 104 - 2 , 104 - 3 , 104 - 4 , and 104 - 5 fluidly communicate with a confluence flow passage 150 - 2 .
  • the diffuser flow passages 104 - 1 , 104 - 8 , 104 - 7 , and 104 - 6 are set to be a group 1
  • the diffuser flow passages 104 - 2 , 104 - 3 , 104 - 4 , and 104 - 5 are set to be a group 2
  • the fluid having passed through the diffuser flow passages 104 of the groups 1 and 2 passes through the respective confluence flow passages 150 , crossover flow passages 200 , and return flow passages 250 , and is supplied to the impeller of the next stage.
  • FIG. 5 is a plan view showing one of the diffuser flow passages 104 according to one embodiment.
  • a curved line that connects centers of circles inscribed in the two diffuser vanes 102 is defined as a flow passage center of the diffuser flow passage 104 .
  • a cross section perpendicular to the flow passage center located on an upstream-most side is defined as the inlet 106 of the diffuser flow passage 104 .
  • a cross section perpendicular to the flow passage center located on a downstream-most side is defined as the outlet 108 of the diffuser flow passage 104 .
  • a flow passage cross-sectional area of the diffuser flow passage 104 is increased from the inlet 106 toward the outlet 108 of the diffuser flow passage 104 .
  • at least a part of the plurality of diffuser flow passages 104 in the same group has a shape different from the other diffuser flow passages 104 in the same group. More specifically, levels of increase of the flow passage cross-sectional areas of the diffuser flow passages 104 are different from each other. For example, the areas of the cross sections of the diffuser flow passages 104 perpendicular to the flow passage center with the same distance from the inlet 106 of the each diffuser flow passage 104 are different from each other.
  • the diffuser flow passage 104 can be configured so that the level of increase of the flow passage cross-sectional area becomes larger as the diffuser flow passage 104 is located closer to the crossover flow passage 200 that fluidly communicates with the confluence flow passage 150 .
  • the crossover flow passage 200 is located close to the diffuser flow passages 104 - 1 and 104 - 5 .
  • the diffuser flow passages 104 - 1 and 104 - 5 close to the crossover flow passage 200 are larger than the other diffuser flow passages 104 - 2 , 104 - 3 , 104 - 4 , 104 - 6 , 104 - 7 , and 104 - 8 in the levels of increase of the flow passage cross-sectional areas.
  • FIG. 6 is a graph showing a relative size of a cross-sectional area of each position of each of the diffuser flow passages 104 - 1 to 104 - 8 .
  • a horizontal axis represents each of the positions P 01 to P 06 of the diffuser flow passage shown in FIG. 5 . Note that the position P 01 corresponds to the inlet 106 of the diffuser flow passage 104 , and that the position P 06 corresponds to the outlet 108 of the diffuser flow passage 104 .
  • a vertical axis of the graph of FIG. 6 represents a relative flow passage cross-sectional area in a case where the cross-sectional area of the position P 01 of the one diffuser flow passage 104 used as a comparative example is set to be 100.
  • the diffuser flow passage 104 has a relatively large region, small region, and large region in increase rates of the cross-sectional areas from the inlet 106 toward the outlet 108 of the diffuser flow passage 104 .
  • an increase rate of a cross-sectional area of the diffuser flow passage 104 - 5 close to the crossover flow passage 200 is large from the positions P 01 to P 02 , becomes relatively smaller from the positions P 02 to P 03 , and becomes larger again from the positions P 03 to P 04 .
  • the diffuser flow passage 104 is configured as described above, and thereby a mixing loss can be reduced when the fluids from the other diffuser flow passages 104 are made to join each other in the confluence flow passage 150 .
  • the diffuser flow passages 104 - 1 , 104 - 8 , 104 - 7 , 104 - 6 of the group 1 and the diffuser flow passages 104 - 5 , 104 - 4 , 104 - 3 , and 104 - 2 of the group 2 may be formed in shapes of rotation symmetry, respectively.
  • FIGS. 7 and 8 are views showing one example of cross-sectional shapes of the diffuser flow passage 104 according to one embodiment.
  • FIG. 7 is a perspective view of a cross section of the diffuser flow passage 104 , and schematically shows the cross-sectional shapes in the positions P 01 to P 06 .
  • the diffuser vanes 102 of a front side are shown by broken lines in FIG. 7 .
  • FIG. 8 shows the each cross-sectional shape in the positions P 01 to P 06 shown in FIG. 7 , respectively.
  • an upper side is the shroud 110 side
  • a lower side is the hub 109 side.
  • the wall surface 110 at the shroud side of the diffuser flow passage 104 has the convex portion at the positions P 01 and P 02
  • the wall surface 109 at the hub side has the convex portion at the position P 03
  • the wall surfaces 109 , 110 at the hub side and the shroud side have the convex portions at the positions P 04 to P 06 .
  • the cross-sectional shape in each position of the diffuser flow passage 104 can be arbitrary, and can be set to be a different one in the other embodiment.
  • the cross-sectional shape of the diffuser flow passage 104 can be set to be an arbitrary one to have the convex portion only on the wall surface 110 at the shroud side, have the convex portion only on the wall surface 109 at the hub side, and to have the convex portions on both of the wall surfaces 109 , 110 at the shroud side and the hub side, from the inlet 106 toward the outlet 108 of the diffuser flow passage 104 .
  • a graph shown in FIG. 9 shows a result of having determined a flow rate per unit time of each diffuser flow passage by a Computational Fluid Dynamics (CFD) in a pump including a diffuser flow passage according to one embodiment of the present invention, and a pump including a diffuser flow passage according to a comparative example.
  • a horizontal axis indicates the diffuser flow passages 104 - 1 to 104 - 8 shown in FIG. 4
  • a vertical axis represents a relative flow rate in each of the diffuser flow passages 104 - 1 to 104 - 8 .
  • the relative flow rate is 1, it means that the fluid with the same flow rate flows through all the diffuser flow passages 104 - 1 to 104 - 8 .
  • all the diffuser flow passages have the same cross sections as those of the comparative example shown in FIG. 6 , and confluence flow passages are the same as those of an example shown in FIG. 9 .
  • cross sections of each of the diffuser flow passages 104 - 1 to 104 - 8 in the example of the present invention are formed as shown in FIG. 6 .
  • the cross-sectional shape is changed for each of the diffuser flow passages 104 - 1 to 104 - 8 , and thereby variation in the flow rates in the respective diffuser flow passages 104 - 1 to 104 - 8 is small. Namely, a mixing loss in the confluence flow passage 150 located on the downstream of the diffuser flow passage 104 is decreased in the embodiment of the present disclosure, compared with the case of the comparative example where all shapes of the diffuser flow passages 104 are the same as each other.
  • FIG. 10 is a view showing a result indicating pressure losses of the diffuser flow passage 104 and the confluence flow passage 150 by the above-described CFD.
  • magnitude of the pressure loss is shown by a gray scale, and a deeper gray scale indicates that a larger pressure loss is present.
  • the pressure loss of the embodiment of the present disclosure is smaller as a whole than that of the case of the comparative example.
  • FIG. 11 is a view showing a flow velocity of the fluid in each of the cross-sectional positions P 01 to P 06 of the diffuser flow passage 104 - 5 according to the comparative example.
  • FIG. 12 is a view showing a flow velocity of the fluid in each of the cross-sectional positions P 01 to P 06 of the diffuser flow passage 104 - 5 according to the embodiment of the present disclosure.
  • the flow velocity in each of the cross-sectional positions P 01 to P 06 is shown by iso-flow velocity lines, and the iso-flow velocity lines indicates that the closer to a center of the cross section, the larger the flow velocity is there. As is understood from FIGS.
  • distortion of the iso-flow velocity line is smaller than that of the comparative example, and the graph in FIG. 12 shows a distribution of the flow velocities in which regularly distributed curves are overlapped. Therefore, in the embodiment of the present disclosure, a flow of the fluid that passes through the diffuser flow passage is uniform, and a rectifying effect is improved. According to the embodiment of the present disclosure, noise and vibration in the pump can be reduced by enhancing the lowering of the pressure loss and the 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)
US15/563,361 2015-03-30 2016-03-24 Fluid machine including diffuser Abandoned US20180080471A1 (en)

Applications Claiming Priority (3)

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JP2015-068481 2015-03-30
JP2015068481 2015-03-30
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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JP (1) JP6706248B2 (ja)
CN (1) CN107949705B (ja)
WO (1) WO2016158636A1 (ja)

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US20180238332A1 (en) * 2015-08-10 2018-08-23 Nuovo Pignone Tecnologie Srl Centrifugal pump
US20230033121A1 (en) * 2018-05-18 2023-02-02 Franklin Electric Co., Inc. Impeller Assemblies and Method of Making

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JP7469990B2 (ja) * 2020-08-07 2024-04-17 日立Astemo株式会社 ２段遠心ポンプ
CN112049822A (zh) * 2020-09-28 2020-12-08 烟台阳光泵业有限公司 多流道导流体及使用该导流体的悬臂式离心泵

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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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Publication number Priority date Publication date Assignee Title
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

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20180238332A1 (en) * 2015-08-10 2018-08-23 Nuovo Pignone Tecnologie Srl Centrifugal pump
US11555496B2 (en) * 2015-08-10 2023-01-17 Nuovo Pignone Tecnologie Srl Centrifugal pump
US20230033121A1 (en) * 2018-05-18 2023-02-02 Franklin Electric Co., Inc. Impeller Assemblies and Method of Making
US11988223B2 (en) * 2018-05-18 2024-05-21 Franklin Electric Co., Inc. Impeller assemblies and method of making

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JP6706248B2 (ja) 2020-06-03
CN107949705B (zh) 2020-03-17
JPWO2016158636A1 (ja) 2018-01-25
WO2016158636A1 (ja) 2016-10-06
EP3279479A1 (en) 2018-02-07
CN107949705A (zh) 2018-04-20
EP3279479A4 (en) 2018-12-12

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