WO2023095638A1 - Pompe centrifuge, dispositif à pompe centrifuge, et automobile de lutte contre l'incendie - Google Patents

Pompe centrifuge, dispositif à pompe centrifuge, et automobile de lutte contre l'incendie Download PDF

Info

Publication number
WO2023095638A1
WO2023095638A1 PCT/JP2022/042022 JP2022042022W WO2023095638A1 WO 2023095638 A1 WO2023095638 A1 WO 2023095638A1 JP 2022042022 W JP2022042022 W JP 2022042022W WO 2023095638 A1 WO2023095638 A1 WO 2023095638A1
Authority
WO
WIPO (PCT)
Prior art keywords
centrifugal pump
centrifugal
inlet
liquid
centrifugal impeller
Prior art date
Application number
PCT/JP2022/042022
Other languages
English (en)
Japanese (ja)
Inventor
拓真 川原
和芳 宮川
Original Assignee
株式会社モリタ
学校法人早稲田大学
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 株式会社モリタ, 学校法人早稲田大学 filed Critical 株式会社モリタ
Priority to ATA9258/2022A priority Critical patent/AT526707A5/de
Priority to CN202280058907.6A priority patent/CN117881899A/zh
Publication of WO2023095638A1 publication Critical patent/WO2023095638A1/fr

Links

Images

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
    • F04D29/18—Rotors
    • F04D29/22—Rotors specially for centrifugal pumps
    • F04D29/2261—Rotors specially for centrifugal pumps with special measures
    • F04D29/2277—Rotors specially for centrifugal pumps with special measures for increasing NPSH or dealing with liquids near boiling-point
    • 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
    • F04D29/40—Casings; Connections of working fluid
    • F04D29/42—Casings; Connections of working fluid for radial or helico-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

Definitions

  • the present invention relates to a centrifugal pump, a centrifugal pump device, and a fire engine.
  • Patent Literature 1 discloses a high-lift pump having a suction flow path that pre-swirls the suction liquid in the direction opposite to the rotation of the impeller.
  • the volute shape of the suction flow path is formed so as to obtain a flow having a swirling component in the direction opposite to the rotational direction of the impeller at the volute outlet, ie, the impeller inlet.
  • Patent Document 2 the lower bearing and the shaft seal device are abolished, the pump structure is an overhang type, the impeller is a single suction impeller fixed to the main shaft by a split ring, and an inducer is arranged in front of the impeller.
  • a centrifugal pump having a barrel-shaped pump casing and a pre-swirl chamber is disclosed.
  • Patent Document 3 discloses a double-suction centrifugal pump having a reverse pre-swirl structure in which upper and lower divided casings are connected by a horizontal flange to be integrated.
  • Patent Document 4 discloses a water suction port for connecting a water suction hose and a water discharge port for connecting a water discharge hose for the purpose of reducing water flow resistance in a water suction pipe, improving cavitation performance, and shortening the time until the start of water discharge.
  • a water suction pipe connecting the water suction port to the pump suction port of the pump, a check valve connected to the pump discharge port of the pump, and a water discharge pipe connecting the check valve to the water discharge port, wherein the water suction pipe is
  • the diffuser joint has a passage cross-sectional area larger on the pump side than the passage cross-sectional area on the water intake side.
  • JP-A-6-123298 Microfilm of Japanese Utility Model Application No. 61-66926 (Japanese Utility Model Application No. 62-179394) JP 2011-252477 A JP 2017-70720 A
  • an object of the present invention is to provide a centrifugal pump that is highly efficient, has excellent suction performance, and can be downsized, a centrifugal pump device that includes the centrifugal pump, and a fire truck that includes the centrifugal pump device.
  • the centrifugal pumps 1A and 1B of the present invention described in claim 1 include a centrifugal impeller 10, inlet casings 20A and 20B connected to the suction port of the centrifugal impeller 10, and an outlet casing 30A connected to the discharge port of the centrifugal impeller 10. , 30B, a curved diffuser 50 provided between the centrifugal impeller 10 and the outlet casings 30A, 30B and having guide vanes 51, and swirling parts 23A, 23B for swirling the liquid flowing into the centrifugal impeller 10.
  • the centrifugal impeller 10 in the centrifugal pumps 1A and 1B of the first aspect, includes a hub 11 fixed to a rotating shaft 16 and a plurality of main blades 12 arranged in the circumferential direction. , and a shroud 14 covering the main wing 12.
  • the guide vane 51 has an inclination angle of more than 0 degrees and 10 degrees or less in the meridional flow direction from the hub 11 side on the leading edge side 51a, and the shroud 14 on the trailing edge side 51b. It is characterized by a shape having an inclination angle of more than 0 degrees and 10 degrees or less in the meridional flow direction from the side. According to the present invention of claim 3, in the centrifugal pumps 1A and 1B of claim 2, in the centrifugal impeller 10, splitter blades 13 having a shorter length than the main blades 12 are provided between the main blades 12.
  • the lean angle ⁇ of the trailing edge of the main blade 12 and the splitter blade 13 is 2 degrees or more and 7 degrees or less from the hub 11 side to the shroud 14 side.
  • a plurality of sheets of The pipe internal swirl portion 23B is provided with stationary blades arranged in an annular shape.
  • one end of the stationary blade is fixed to the inlet pipe 24, and the other end of the stationary blade is capped on the tip of the rotating shaft 16 of the centrifugal impeller 10. 17 is fixed.
  • the cap 17 has a streamlined shape with a larger diameter on the downstream side than on the upstream side.
  • an inducer 40 is provided between the in-pipe swirl portion 23B and the centrifugal impeller 10, and the inducer The rotation direction of 40 is characterized in that it is the same as the direction in which the liquid is swirled by the in-pipe swirl portion 23B.
  • the swirl portion is provided in the inlet casing 20A to circulate the liquid along the circumferential direction of the centrifugal impeller 10.
  • the inlet casing 20A includes a first inlet 21 which is one inlet of the casing internal swirling part 23A and the other of the casing internal swirling part 23A.
  • the swirl direction of the liquid entering from the first inlet part 21 and flowing into the centrifugal impeller 10, and the swirling direction of the liquid entering from the second inlet part 22 and flowing into the centrifugal impeller 10 is the same as the direction of rotation of the centrifugal impeller 10 .
  • the casing-inside swirl portion 23A has a curved shape along the circumferential direction of the centrifugal impeller 10.
  • the outlet casing 30A includes an outflow portion 33 for guiding liquid flowing out of the centrifugal impeller 10 to the outlet, and one of the outflow portion 33. and a second outlet portion 32 that is the other outlet of the outflow portion 33.
  • the outflow portion 33 has a curved shape along the circumferential direction of the centrifugal impeller 10.
  • the centrifugal pump device of the present invention has a centrifugal pump 1A according to any one of claims 8 to 10, and a liquid suction hose connection part 61 to which a liquid suction hose is connected to one end. It has a liquid suction pipe 60 whose other end is connected to the inlet casing 20A of the centrifugal pump 1A, a liquid discharge hose connection portion 71 to which a liquid discharge hose is connected at one end, and an outlet of the centrifugal pump 1A at the other end.
  • a liquid discharge pipe 70 connected to the casing 30A, the liquid suction pipe 60 is arranged in line with the inlet casing 20A, and the liquid discharge pipe 70 is arranged in line with the outlet casing 30A.
  • an ejector device is provided for discharging the gas in the liquid suction hose connected to the liquid suction hose connecting portion 61 to the inlet casing 20A.
  • the tube axis center 60x of the liquid suction pipe 60 and the tube axis center 70x of the liquid discharge pipe 70 are positioned at the same height.
  • the liquid discharge pipe 70 is provided with a one-way check valve 80 .
  • the fire engine of the present invention according to claim 15 is the centrifugal pump 1A or 1B according to any one of claims 1 to 10, or the centrifugal pump according to any one of claims 11 to 14. It is characterized by being equipped with a pump device.
  • centrifugal pump that is highly efficient, has excellent suction performance, and can be downsized, a centrifugal pump device that includes the centrifugal pump, and a fire truck that includes the centrifugal pump device.
  • FIG. 1 is an external view of a centrifugal pump according to a first embodiment of the present invention
  • FIG. Internal configuration diagram of the same centrifugal pump Diagram showing the flow on the inlet side of the centrifugal pump Diagram showing the same inducer Diagram showing the same centrifugal impeller Enlarged view of the part where the same curved diffuser is provided
  • FIG. 2 is an external view of a centrifugal pump according to a second embodiment of the present invention
  • Internal configuration diagram of the same centrifugal pump Diagram showing the inlet pipe and swirling part inside the pipe
  • Comparison diagram of meridional plane shape for the centrifugal pump according to the first embodiment Comparison chart of pump performance Diagram showing the suction performance of the same centrifugal pump Layout of the centrifugal pump device mounted on the same fire engine
  • Comparison diagram of the layout of the same liquid absorption piping and liquid discharge piping Comparison diagram of the same check valve
  • Explanatory diagram of ejector pumping in the same centrifugal pump device Diagram of one side discharge of the same centrifugal pump Explanatory drawing of ejector pumping water in a conventional centrifugal pump device
  • the centrifugal pump according to the first embodiment of the present invention includes a centrifugal impeller, an inlet casing connected to the suction port of the centrifugal impeller, an outlet casing connected to the outlet port of the centrifugal impeller, and a combination of the centrifugal impeller and the outlet casing.
  • a curved diffuser having guide vanes provided therebetween and a swirling section for swirling the liquid flowing into the centrifugal impeller, the curved diffuser being curved from the radial direction to the axial direction of the centrifugal impeller, and the flow area gradually increasing downstream
  • the reducing and swirling part swirls the liquid in the same direction as the direction of rotation of the centrifugal impeller.
  • the centrifugal impeller in the centrifugal pump according to the first embodiment, includes a hub fixed to the rotating shaft, a plurality of main blades arranged in the circumferential direction, and covering the main blades. and the guide vanes have an inclination angle of greater than 0 degrees and less than or equal to 10 degrees in the meridional flow direction from the hub side on the leading edge side and greater than 0 degrees in the meridional flow direction from the shroud side on the trailing edge side. It has a shape with an inclination angle of 10 degrees or less. According to this embodiment, the pump efficiency can be further improved.
  • the centrifugal impeller in the centrifugal pump according to the second embodiment, is provided with splitter blades shorter in length than the main blades between the main blades. and the lean angle of the trailing edge of the splitter blade is 2 degrees or more and 7 degrees or less from the hub side to the shroud side. According to this embodiment, the pump efficiency can be further improved. Moreover, the turbulence of the flow caused by making the centrifugal pump smaller than before can be improved.
  • a plurality of stationary blades are provided inside the inlet pipe connected to the inlet casing as the swirling section. is provided with an inner pipe swirl portion arranged in an annular shape, and the flow passage area of the inner pipe swirl portion gradually decreases toward the downstream side.
  • the swirling section that swirls the liquid before flowing into the centrifugal impeller can be configured relatively simply.
  • the flow passage area in the swirl portion gradually decreases toward the downstream side, it is possible to improve the turbulence of the flow caused by the arrangement of the stationary blades.
  • one end of the stator vane is fixed to the inlet pipe, and the other end is attached to a cap placed on the tip of the rotating shaft of the centrifugal impeller. It is fixed.
  • the present embodiment by fixing both ends of the stationary blade to other members, it is possible to reduce the thickness of the stationary blade while securing the strength, thereby stably generating a swirling flow.
  • the longitudinal length (length in the axial direction) of the centrifugal pump becomes longer due to the provision of the stator vanes. can be suppressed.
  • the cap in the centrifugal pump according to the fifth embodiment, has a streamlined shape with a larger diameter on the downstream side than on the upstream side. According to this embodiment, it is possible to suppress flow turbulence caused by the arrangement of the stationary blades.
  • an inducer is provided between the in-pipe swirl portion and the centrifugal impeller, and the rotation direction of the inducer is is the same as the direction in which the liquid is swirled by the swirling part in the pipe. According to the present embodiment, it is possible to suppress the occurrence of cavitation in the centrifugal impeller and delay reaching the cavitation performance limit.
  • the inlet casing serves as a swirling section to swirl the liquid along the circumferential direction of the centrifugal impeller.
  • the inlet casing has a first inlet which is one inlet of the casing-inside swirl part and a second inlet which is the other inlet of the casing-inside swirl part. and the swirling direction of the liquid entering from the first inlet and flowing into the centrifugal impeller and the swirling direction of the liquid entering from the second inlet and flowing into the centrifugal impeller are the same as the rotating direction of the centrifugal impeller.
  • a swirl flow can be generated in the inlet casing, and the fluid flows into the centrifugal impeller radially rather than axially, so the piping layout can be simplified.
  • the swirl portion inside the casing is curved along the circumferential direction of the centrifugal impeller. According to this embodiment, the liquid flowing into the centrifugal impeller can be reliably swirled, and the size of the centrifugal pump can be reduced and the number of pipes can be reduced.
  • the outlet casing includes an outlet section for guiding the liquid that has flowed out of the centrifugal impeller to the outlet, and one outlet of the outlet section. and a second outlet that is the other outlet of the outflow section, and the outflow section is an outlet spiral-shaped section curved along the circumferential direction of the centrifugal impeller.
  • a centrifugal pump device has a centrifugal pump according to any one of the eighth to tenth embodiments, and a liquid suction hose connection part to which a liquid suction hose is connected to one end.
  • the liquid suction pipe is arranged in line with the inlet casing, and the liquid discharge pipe is arranged in line with the outlet casing.
  • the length of the piping can be made shorter than in the conventional art, leading to a reduction in the weight of the piping.
  • the size of the pump device can be reduced to increase the degree of freedom in layout of piping and the like.
  • an ejector device for discharging gas in the liquid suction hose connected to the liquid suction hose connecting portion to the inlet casing
  • the ejector The device has a vapor phase suction pipe having one end connected to the liquid suction hose connection side of the liquid suction hose connection part and the other end connected to the inlet casing, and the other end of the gas phase suction pipe is connected to the inlet In the casing, it is connected to a position axially farther from the centrifugal impeller than the part where the backflow from the centrifugal impeller occurs, or to the inner diameter side of the part where the backflow occurs.
  • the number of options for connecting the other end of the vapor-phase suction pipe increases, so the degree of freedom in connection can be increased.
  • the center of the pipe axis of the liquid suction pipe and the center of the pipe axis of the liquid discharge pipe are positioned at the same height.
  • the piping layout can be further simplified, and the piping weight can be further reduced and the loading space can be secured.
  • the liquid discharge pipe is provided with a one-way check valve. According to this embodiment, the energy loss caused by the check valve can be reduced, and the efficiency of the pump device can be improved.
  • the fire truck according to the fifteenth embodiment of the present invention includes the centrifugal pump according to any one of the first to tenth embodiments or the centrifugal pump device according to any one of the eleventh to fourteenth embodiments. It is installed. According to this embodiment, it is possible to provide a fire engine mounted with a centrifugal pump or a centrifugal pump device that is more efficient and has better suction performance than the conventional one, and that has a reduced size.
  • FIG. 1A and 1B are perspective views of the centrifugal pump according to the first embodiment
  • FIG. 1A is a perspective view seen from the inlet casing side
  • FIG. c) is a side view.
  • FIG. 2 is an internal configuration diagram of the centrifugal pump.
  • FIG. 3 is a diagram showing the flow on the inlet side of the centrifugal pump.
  • a centrifugal pump 1A includes a centrifugal impeller 10, an inlet casing 20A connected to the suction port of the centrifugal impeller 10, an outlet casing 30A connected to the discharge port of the centrifugal impeller 10, and an inlet casing 20A. It has an inducer 40 provided between the centrifugal impeller 10 and a curved diffuser 50 provided between the centrifugal impeller 10 and the outlet casing 30A. Centrifugal impeller 10 is positioned between inlet casing 20A and outlet casing 30A. Moreover, the bearing box 15 accommodating the rotating shaft 16 of the centrifugal impeller 10 is arranged on the outlet casing 30A side.
  • the inlet casing 20A includes an in-casing swirl portion 23A as a swirl portion, a first inlet portion 21 as one inlet of the in-casing swirl portion 23A, and a second inlet portion 22 as the other inlet of the in-casing swirl portion 23A.
  • the inlet 21a of the first inlet section 21 is oriented in one direction
  • the inlet 22a of the second inlet section 22 is oriented in the other direction.
  • the direction of the inflow port 21a of the first inlet portion 21 and the direction of the inflow port 22a of the second inlet portion 22 differ from each other by approximately 180 degrees in the horizontal direction.
  • the conduit diameter (inner diameter) of the first inlet portion 21 and the second inlet portion 22 is, for example, 120 to 160 mm.
  • the in-casing swirl portion 23 ⁇ /b>A is an inlet spiral-shaped portion curved along the circumferential direction of the centrifugal impeller 10 .
  • the casing internal swirl portion 23A (inlet spiral shape portion) causes the liquid entering from the first inlet portion 21 and the second inlet portion 22 to flow into the centrifugal impeller 10 from the radial direction while being pre-swirled by the generated angular momentum.
  • the centrifugal pump 1A according to this embodiment can generate a swirling flow within the inlet casing 20A.
  • the white arrow indicates the flow direction of the liquid entering from the first inlet 21
  • Wa indicates the inflow position of the liquid entering from the first inlet
  • the black arrow indicates the entering from the second inlet 22.
  • the flow direction of the liquid is shown, and Wb shows the inflow position of the liquid which entered from the 2nd inlet part 22.
  • Wb shows the inflow position of the liquid which entered from the 2nd inlet part 22.
  • the positions at which the liquid flows into the centrifugal impeller 10 from the radial direction differ by approximately 180 degrees between the liquid entering from the first inlet portion 21 and the liquid entering from the second inlet portion 22 .
  • the swirling direction of the liquid entering from the first inlet portion 21 and flowing into the centrifugal impeller 10 is the same as the swirling direction of the liquid entering from the second inlet portion 22 and flowing into the centrifugal impeller 10 .
  • the liquid flows in the circumferential direction of the centrifugal impeller 10.
  • the swirling portion 23A in the casing can be swirled as in the present embodiment, so that the liquid flowing into the centrifugal impeller 10 can be swirled reliably. It is possible to reduce the size of 1A and reduce the number of pipes.
  • the area change rate of the flow path of the casing-inside swirl portion 23A continuing from the first inlet portion 21 and the flow path of the casing-inside swirl portion 23A continuing from the second inlet portion 22 is determined by the angular momentum of the flowing fluid.
  • the outlet casing 30 ⁇ /b>A includes an outlet section 33 , a first outlet section 31 that is one outlet of the outlet section 33 , and a second outlet section 32 that is the other outlet of the outlet section 33 .
  • the outflow port 31a of the first outlet portion 31 is oriented in one direction
  • the outflow port 32a of the second outlet portion 32 is oriented in the other direction.
  • the orientation of the outflow port 31a of the first outlet portion 31 and the orientation of the outflow port 32a of the second outlet portion 32 differ from each other by approximately 180 degrees in the horizontal direction.
  • the conduit diameter (inner diameter) of the first outlet portion 31 and the second outlet portion 32 is, for example, 60 to 90 mm.
  • the outflow portion 33 is an outlet spiral portion curved along the circumferential direction of the centrifugal impeller 10 .
  • the outflow portion 33 (outlet spiral shape portion) guides the liquid that has flowed out of the centrifugal impeller 10 to the first outlet portion 31 and the second outlet portion 32 .
  • the positions from which the liquid flows out radially from the centrifugal impeller 10 are substantially 180 degrees different between the flow path toward the first outlet portion 31 and the flow path toward the second outlet portion 32 .
  • the outflow part 33 may have a volute shape having one outlet upward, or a structure in which the fluid flows out in the axial direction. can flow out in the radial direction, the size of the centrifugal pump 1A can be reduced and the number of pipes can be reduced.
  • the area change rate of the flow path of the outflow portion 33 leading to the first outlet portion 31 and the flow path of the outflow portion 33 leading to the second outlet portion 32 is determined by the angular momentum of the inflowing fluid.
  • FIG. 4 is a front view of the inducer.
  • the inducer 40 which is an axial flow impeller, it is possible to suppress the occurrence of cavitation in the centrifugal impeller 10 and delay reaching the cavitation performance limit.
  • a forced vortex inducer that is proportional to the radius of the circumferential component of the flow velocity of the fluid flowing in the centrifugal pump 1A, or a free vortex inducer that is inversely proportional to the radius can be used. It is possible, but preferably of the forced vortex type. By applying the forced vortex inducer, the diameter of the inducer 40 on the hub 42 side is reduced, making it easier to secure the head of the entire centrifugal pump 1A.
  • the blades 41 of the inducer 40 stand in the axial direction, and the gap between the blades 41 is increased. It is possible to increase the gap between Thereby, the breakdown flow rate can be increased. Also, the suction performance of the inducer 40 is improved.
  • FIG. 5 shows a centrifugal impeller
  • FIG. 5(a) is a front view
  • FIG. 5(b) is a view indicated by arrow A in FIG. 5(a).
  • the centrifugal impeller 10 includes a hub 11 fixed to a rotating shaft 16, a plurality of main wings 12 arranged in the circumferential direction, and a splitter arranged between the main wings 12 and shorter than the main wings 12. It has a wing 13 and a shroud 14 covering the main wing 12 .
  • the main wings 12 and splitter wings 13 are alternately arranged.
  • FIG. 5B shows the lean angle ⁇ (dihedral angle) of the main wing 12 and splitter wing 13 .
  • the lean angle ⁇ of the trailing edges of all the main blades 12 and the lean angle ⁇ of the trailing edges of the splitter blades 13 in the centrifugal impeller 10 are the same.
  • the lean angle ⁇ is set in consideration of the flow on the downstream side, such as the shape of the curved diffuser 50. It is more preferable that the angle is 4 degrees or more and 5 degrees or less in the flow direction from the side to the shroud 14 side. Thereby, the meridional velocity distribution from the hub 11 to the shroud 14 can be set to a predetermined velocity distribution, and the pump efficiency can be further improved.
  • FIG. 6 is an enlarged view of a portion of the centrifugal pump in FIG. 2 where a curved diffuser is provided.
  • the curved diffuser 50 has guide vanes 51, is curved from the radial direction to the axial direction of the centrifugal impeller 10, and the flow area gradually decreases toward the downstream.
  • the guide vanes 51 have an inclination angle of more than 0 degrees and 10 degrees or less in the meridional flow direction from the hub 11 side to the shroud 14 side on the leading edge side 51a that is the inlet side, and the inclination angle is greater than 0 degrees and 10 degrees or less on the trailing edge side 51b that is the outlet side.
  • the shape has an inclination angle of more than 0 degree and 10 degrees or less in the meridional flow direction from the side to the hub 11 side. More preferably, the tilt angle on the leading edge side 51a is 3 degrees or more and 5 degrees or less, and the tilt angle on the trailing edge side 51b is 1 degree or more and 3 degrees or less.
  • the "meridional plane flow direction" is the flow direction when the flow in the pump is projected onto the meridional plane. Thereby, the pump efficiency can be further improved.
  • the inclination angle of the leading edge side 51a and the inclination angle of the trailing edge side 51b may be the same 3 degrees.
  • FIG. 7A and 7B are external views of a centrifugal pump according to the second embodiment, FIG. 7A is a side view, FIG. 7B is a front view, FIG. 7C is a rear view, and FIG. 7D is a It is a bottom view.
  • FIG. 8 is an internal configuration diagram of the centrifugal pump.
  • the centrifugal pump 1B includes a centrifugal impeller 10, an inlet casing 20B connected to the suction port of the centrifugal impeller 10, an inlet pipe 24 connected to the inlet of the inlet casing 20B, and a discharge port of the centrifugal impeller 10.
  • An outlet casing 30B connected to the outlet, an inducer 40 provided upstream of the centrifugal impeller 10, and a curved diffuser 50 provided between the centrifugal impeller 10 and the outlet casing 30B.
  • Centrifugal impeller 10 is positioned between inlet casing 20B and outlet casing 30B.
  • the bearing box 15 accommodating the rotating shaft 16 of the centrifugal impeller 10 is arranged on the outlet casing 30B side.
  • the centrifugal impeller 10 has a hub 11 fixed to a rotating shaft 16, a plurality of main wings 12 arranged in the circumferential direction, and a plurality of main wings 12 arranged between the main wings 12, as in the first embodiment described above. It has splitter blades 13 shorter in length than the main wings 12 and shrouds 14 covering the main wings 12, and the main wings 12 and the splitter blades 13 are alternately arranged.
  • the tip of the rotary shaft 16 is covered with a cap 17 .
  • the tip of the cap 17 protrudes from the upstream end of the inlet pipe 24 .
  • the inlet casing 20B has a substantially circular shape when viewed from the front, and has a through hole through which the rotating shaft 16 of the centrifugal impeller 10 and the fluid pass are formed in the center of the circular shape. Liquid enters the centrifugal impeller 10 axially.
  • the outlet casing 30B has a substantially circular shape when viewed from the front, and a through hole through which the rotating shaft 16 of the centrifugal impeller 10 passes is formed in the center of the circular shape.
  • the outlet casing 30B has a volute shape with one upwardly facing outlet 30Ba, and the liquid entering the outlet casing 30B from the centrifugal impeller 10 flows in the circumferential direction and is discharged from the outlet 30Ba.
  • FIG. 9A and 9B are views showing an inlet pipe and a swirling part in the pipe
  • FIG. 9A is a front view
  • FIG. 9B is a rear view
  • FIG. 9C is a cross section AA of FIG. It is a diagram.
  • the inlet pipe 24 is a straight pipe, and its upstream end is connected to the liquid absorption pipe 60 (see FIG. 13) by flange connection or the like, and its downstream end is connected to the inlet casing 20B.
  • an in-pipe turning portion 23B is provided as a turning portion.
  • the in-pipe swirl portion 23B is formed by arranging a plurality of twisted stationary blades in a ring, and swirls the passing liquid in one direction.
  • each blade can be set as appropriate, but in this embodiment, the thickness of each blade is constant from the base end to the tip, and the curvature on the base end side is larger than the curvature on the tip side. are doing.
  • the swirling direction of the liquid by the in-pipe swirling section 23B is the same as the rotating direction of the centrifugal impeller 10. By allowing the pre-swirled liquid to flow into the centrifugal impeller 10, the efficiency is higher than in the conventional art, and A centrifugal pump with excellent suction performance can be realized. Further, by using the in-pipe swirl portion 23B as the swirl portion, the liquid can be pre-swirled with a relatively simple configuration.
  • One end (tip) of the stationary blade that constitutes the in-pipe swirl portion 23B is fixed to the inner surface of the inlet pipe 24, and the other end (base end) is fixed to the outer surface of the cap 17 of the centrifugal impeller 10.
  • FIG. By fixing both ends of the stationary blade to other members in this way, it is possible to reduce the thickness of the stationary blade while ensuring strength, prevent the stationary blade from wobbling, and stably generate a swirling flow.
  • the longitudinal length (length in the axial direction) of the centrifugal pump 1B is increased by providing the stator vane
  • the cap 17 also serves as the fixing destination of the other end of the stator vane, thereby suppressing the increase in length. be able to. As shown in FIG.
  • the cap 17 has a streamlined shape with a larger diameter on the downstream side than on the upstream side, and as a result, the flow passage area where the swirl portion 23B in the pipe is provided gradually decreases toward the downstream side.
  • the blade length on the upstream side is larger than the blade length on the downstream side.
  • the combination of the in-pipe swirl portion 23B composed of the stationary blades and the streamline-shaped (cannonball-shaped) cap 17 can generate a stable swirl flow, and at the same time, the longitudinal length of the centrifugal pump 1B can be increased. It is possible to reduce the size and weight by shortening.
  • the inducer 40 is positioned between the centrifugal impeller 10 and the in-pipe swirl portion 23B.
  • the direction of rotation of the inducer 40 is the same as the direction in which the liquid is swirled by the in-pipe swirl portion 23B.
  • the guide vane 51 has an inclination angle of more than 0 degrees and 10 degrees or less in the meridional flow direction from the hub 11 side to the shroud 14 side on the leading edge side 51a which is the inlet side, and the outlet It is preferable that the trailing edge side 51b has an inclination angle of more than 0 degrees and 10 degrees or less in the meridional flow direction from the shroud 14 side to the hub 11 side. More preferably, the tilt angle on the leading edge side 51a is 3 degrees or more and 5 degrees or less, and the tilt angle on the trailing edge side 51b is 1 degree or more and 3 degrees or less. Thereby, the pump efficiency can be further improved.
  • FIG. 10A is a radial inflow centrifugal pump (Embodiment I) according to a first embodiment of the present invention
  • FIG. It is an inflow type two-stage balance turbine pump (Comparative Example I). Both pumps satisfy the suction conditions of "normal operation with a suction head of -3 m from the pump inlet position", and the pump performance satisfies the "A-2 class" in the ministerial ordinance that defines the technical standards for power fire pumps.
  • the rotational speed of both the centrifugal pump 1A of Example I and the pump of Comparative Example I is 600-3250 rpm.
  • the centrifugal pump 1A of Example I since the liquid flows in the radial direction, it is possible to save the space including the piping. Moreover, since the pressure is increased in one stage, the length in the axial direction can be shortened.
  • FIGS. 11(a) and 11B are comparison diagrams of pump performance, in which FIG. 11(a) shows the head coefficient and FIG. 11(b) shows the efficiency.
  • the horizontal axes in FIGS. 11(a) and 11(b) are flow coefficients.
  • " ⁇ " in Fig. 11(a) is the data of the centrifugal pump 1A of Example I
  • ⁇ is the data of the pump of Comparative Example I
  • " ⁇ " in Fig. 11(b) is the centrifugal pump of Example I. 1A
  • “ ⁇ " is data for the Comparative Example I pump.
  • the flow coefficient ⁇ (phi) is expressed by the following formula (1)
  • the lift coefficient ⁇ (psi) is expressed by the following formula (2)
  • the efficiency ⁇ (epsilon) is expressed by the following formula (3).
  • Q is the flow rate [m 3 /min]
  • H is the head [m]
  • ⁇ is the angular velocity [rad/s]
  • u is the peripheral speed of the impeller outer diameter [m/s]
  • ⁇ is the efficiency of the pump
  • ⁇ 0 is the design point efficiency of Comparative Example I
  • g is the acceleration of gravity [m/s 2 ]
  • ⁇ is the density of the liquid [kg/m 3 ]
  • D is the impeller outlet diameter [m].
  • the centrifugal pump 1A of Example I has a more limited output head than the pump of Comparative Example I, and as shown in FIG. 11(b), the centrifugal pump 1A of Example I shows a clear improvement in efficiency compared to the pump of Comparative Example I.
  • FIG. 12 is a diagram showing the suction performance of the centrifugal pump of Example I.
  • FIG. FIG. 12(a) is a graph of the lift coefficient, where the vertical axis is the lift coefficient and the horizontal axis is the effective suction head (NPSH).
  • 12(b) to (d) show the region where cavitation occurs near the centrifugal impeller.
  • the centrifugal pump 1A of Example I and the pump of Comparative Example I are compared with respect to suction performance.
  • Effective suction head (NPSH(H sv )) is represented by the following equation (4).
  • NPSH at which the head coefficient of the pump drops by 3% from the steady state and pumping becomes impossible is defined as Hsv .
  • the suction specific speed S is represented by the following equation (5) using Hsv .
  • n is the rotation speed [rpm]
  • Q is the flow rate [m 3 /min].
  • the centrifugal pump 1A with higher efficiency and better suction performance than the conventional one is realized. be able to.
  • the piping layout can be simplified.
  • the pre-swirl direction in the same direction as the rotation direction of the centrifugal impeller 10, it is possible to easily achieve high efficiency and suction performance at the same time.
  • FIG. 13A and 13B are layout diagrams of a centrifugal pump device mounted on a fire truck, FIG. 13(a) being a top view and FIG. 13(b) being a side view.
  • the centrifugal pump device includes a centrifugal pump 1A, a liquid suction pipe 60 having a liquid suction hose connection portion 61 to which a liquid suction hose is connected, and a liquid discharge pipe 70 having a liquid discharge hose connection portion 71 to which a liquid discharge hose is connected. and a one-way check valve 80 provided in the discharge pipe 70 .
  • liquid suction hose connections 61 are arranged on the right side and left side of the vehicle body, respectively, and liquid discharge hose connections 71 are arranged on the right side and left side of the vehicle body, respectively. Thereby, the connection of the liquid suction hose and the connection of the liquid discharge hose can be performed from either the left or the right.
  • the liquid suction pipe 60 has a liquid suction hose connection portion 61 at one end and is connected to the inlet casing 20A of the centrifugal pump 1A at the other end. Between one end and the other end of the liquid absorption pipe 60 is connected a branched liquid absorption pipe 62 having a liquid absorption side relay portion 63 at its tip.
  • the liquid-suction-side relay portions 63 are arranged on the right side and the left side of the vehicle body, respectively, and are connected to relay hoses used for relaying fire extinguishing liquid or the like delivered from another fire engine or the like.
  • the liquid discharge pipe 70 has a first liquid discharge hose connection section 71A as a liquid discharge hose connection section 71 at one end, and a second liquid discharge hose connection section 71B located on the vehicle rear side of the first liquid discharge hose connection section 71A. and the other end is connected to the outlet casing 30A of the centrifugal pump 1.
  • the first liquid discharge hose connection portion 71A is provided in a branch liquid discharge pipe 72 connected between one end and the other end of the liquid discharge pipe 70 .
  • the second liquid discharge hose connecting portion 71B is provided on a straight line with the liquid discharge pipe 70 .
  • a relay hose used for relaying fire extinguishing fluid to another fire engine or the like can be connected as a liquid discharge hose to the first liquid discharge hose connection portion 71A and the second liquid discharge hose connection portion 71B.
  • centrifugal pump according to the second embodiment can also be mounted on a fire engine, and the liquid suction pipe 60 and the liquid discharge pipe 70 can be connected toward the side or rear of the fire engine. .
  • FIGS. 14A and 14B are diagrams for comparing the layouts of liquid suction pipes and liquid discharge pipes, and FIG. ), FIG. 14(b) is a side view of the same, FIG. 14(c) is a top view of a conventional axial inflow type centrifugal pump device (comparative example II), and FIG. 14(d) is a side view of the same. be.
  • the black arrows in FIG. 14 indicate the flow on the liquid absorption side, and the white arrows indicate the liquid discharge side.
  • the liquid flowing from the liquid suction pipe 160 is bent from the radial direction to the axial direction and then flows into the centrifugal impeller 10, The liquid flowing out from the centrifugal impeller 10 reaches the liquid discharge hose connecting portion through the liquid discharge pipe 170 which is a bent pipe.
  • the centrifugal pump device of Example II as shown in FIGS. 14(a) and 14(b), the liquid suction pipe 60 is arranged in line with the inlet casing 20A, and the liquid discharge pipe 70 is arranged in line with the outlet casing 30A. placed on a line.
  • the length of the piping can be shortened compared to the conventional one, leading to a reduction in the weight of the piping.
  • the size of the pump device can be reduced, and the degree of freedom in layout can be increased.
  • the height from the installation floor differs between the pipe axis center 160x of the liquid suction pipe 160 and the pipe axis center 170x of the liquid discharge pipe 170.
  • the tube axis center 60x of the liquid suction pipe 60 and the tube axis center 70x of the liquid discharge pipe 70 are positioned at the same height.
  • the liquid suction pipe 60 and the liquid discharge pipe 70 can be laid out on the same plane, and a pipe structure in which only the inlet casing 20A and the outlet casing 30A protrude upward in the entire centrifugal pump device is possible.
  • a pipe structure in which only the inlet casing 20A and the outlet casing 30A protrude upward in the entire centrifugal pump device is possible.
  • FIG. 15A and 15B are comparison diagrams of check valves, and FIG. 15A is an enlarged view of the vicinity of the check valve of the centrifugal pump device of Embodiment II shown in FIGS. 13A and 14A; 14(b) is an enlarged view of the vicinity of the check valve of the centrifugal pump device of Comparative Example II shown in FIG. 14(d), and FIG. 15(c) is a structural drawing of the check valve used in Comparative Example II.
  • the arrow in FIG.15(c) has shown the flow direction of the liquid.
  • the check valve prevents backflow of the liquid discharged from the centrifugal pump, and also prevents air from entering the centrifugal pump from the liquid discharge pipe side when the centrifugal pump is pumped by the vacuum pump.
  • the centrifugal pump device of Comparative Example II uses a so-called T-shaped check valve as shown in FIG. 15(c) due to its piping structure.
  • a T-shaped non-return valve causes a large amount of energy loss because the direction of flow changes.
  • the one-way check valve 80 can be used because the discharge pipe 70 is arranged in line with the outlet casing 30A. The one-way non-return valve 80 does not redirect flow across the valve, thereby reducing energy loss and increasing the efficiency of the centrifugal pumping device.
  • FIG. 16A and 16B are diagrams for explaining ejector pumping in the centrifugal pump device of Example II, in which FIG. 16(a) shows the backflow region and FIG. .
  • FIG. 18 is an explanatory view of ejector pumping in the centrifugal pump device of Comparative Example II, FIG. 18(a) showing the backflow region, and FIG. 18(b) showing the connection point of the other end of the gas phase suction pipe.
  • the centrifugal pump device has an ejector device that discharges the gas in the liquid suction hose connected to the liquid suction hose connecting portion 61 to the inlet casing 20A, and is capable of ejecting water.
  • Ejector pumping is performed to secure a further water discharge flow rate during water discharge, and water is pumped using the difference between the negative pressure immediately before the centrifugal pump 1A and the atmospheric pressure.
  • the ejector device has a vapor phase suction pipe 90 having one end connected to the liquid suction hose connection side (outer than the plug) of the liquid suction hose connecting portion 61 and the other end connected to the inlet casing 20A.
  • the gas filling the liquid suction hose is gradually discharged by the gas phase suction pipe 90 functioning as an ejector pipe to fill the liquid suction hose with the liquid phase.
  • a donut-shaped (annular) backflow region when viewed from the front of the pump is generated in the piping near the inlet side of the centrifugal impeller 10 .
  • a backflow area always occurs, and it is difficult to eliminate the backflow. Since the water pressurized by the centrifugal pump 1A flows backward into the backflow region, it is a great obstacle for the ejector pumping water by the pressure difference with the atmosphere. Therefore, it is necessary to avoid a backflow region at the other end of the vapor phase suction pipe 90 connected to the wall surface of the inlet casing 20A.
  • the inlet casing 20A also has a backflow region on the wall surface on the outer diameter side near the inlet side of the centrifugal impeller 10.
  • the inlet casing 20A has a spiral shape, as shown in FIG. It is possible to connect the other end.
  • the ejector pipe can be provided at a position where the pressure is low while avoiding the donut-shaped backflow region. Further, since the liquid is swirling inside the inlet casing 20A, the pressure in the portion away from the centrifugal impeller 10 is lower than that of the centrifugal pump device of Comparative Example II. Therefore, even if the other end of the gas-phase suction pipe 90 is connected to the position "B" at a predetermined distance from the inlet side of the centrifugal impeller 10 so as to avoid the backflow region, deterioration of the ejector performance can be suppressed.
  • the other end of the gas phase draft line 90 can be connected to the position "A" just before the centrifugal impeller 10, and even if it is connected to the relatively distant position "B" second position. A decrease in ejector performance can be suppressed. Therefore, there are more options for connecting the other end of the vapor-phase suction pipe 90, and the degree of freedom of connection increases.
  • FIGS. 17A and 17B are diagrams related to one-sided discharge of the centrifugal pump
  • FIG. 17A shows a centrifugal pump in a state in which the outflow port 32a of the second outlet portion 32 is blocked and one-sided discharge is performed from the outflow port 31a of the first outlet portion 31.
  • Fig. 17(b), (c) shows the circumferential pressure distribution at the outlet of the centrifugal impeller.
  • the vertical axis is the lift coefficient
  • the horizontal axis is the angle (Degree).
  • Table 1 shows the lift coefficient for double-sided discharge and the lift coefficient for single-sided discharge.
  • FIG. 17(b) the data when discharging from both sides is indicated by a dashed line, and the data when discharging from the outflow port 32a of the completely blocked second outlet portion 32 at the time of discharging from one side is assumed to be 0 for the flow rate coefficient is indicated by a dotted line. is shown.
  • Table 2 shows a performance comparison between double-sided ejection and single-sided ejection.
  • the one-side discharge in which the liquid is discharged from only one of the right side and the left side causes the flow to be biased to either the first outlet portion 31 or the second outlet portion 32.
  • the pump efficiency is reduced compared to double-sided delivery.
  • FIG. 17(c) the data when the discharge flow rate from the outflow port 32a of the second outlet portion 32 completely blocked during one-side discharge is assumed to be 0 is shown by a dotted line.
  • the solid line indicates the data when the discharge flow rate from the outflow port 32a of the opened second outlet portion 32 is assumed to be 0.01.
  • Table 3 shows a performance comparison between the two. As shown in Table 3, it can be seen that even a small amount of flow from the blocked pipe restores pump efficiency. Therefore, it is preferable to connect the left and right pipes (the first outlet portion 31 and the second outlet portion 32) with a bypass pipe to prevent the flow from being biased to one side.

Landscapes

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

Abstract

L'invention concerne une pompe centrifuge (1A, 1B) comprenant : une roue centrifuge (10) ; un carter d'entrée (20A, 20B) qui est relié à un orifice d'admission de la roue centrifuge (10) ; un carter de sortie (30A, 30B) qui est relié à un orifice d'évacuation de la roue centrifuge ; un diffuseur incurvé (50) qui est disposé entre la roue centrifuge (10) et le carter de sortie (30A, 30B) et qui comporte une aube directrice (51) ; et une partie tourbillonnaire (23A, 23B), qui fait tourbillonner un liquide qui s'écoule dans la roue centrifuge (10), le diffuseur incurvé (50) étant incurvé depuis la direction radiale de la roue centrifuge (10) vers la direction axiale et comprenant une zone de trajet d'écoulement qui diminue progressivement vers l'aval, et la partie tourbillonnaire (23A, 23B) faisant tourbillonner le liquide dans la même direction que le sens de rotation de la roue centrifuge (10). Ainsi, la pompe centrifuge (1A, 1B) est très efficace, possède d'excellentes performances d'admission, et permet une réduction de taille.
PCT/JP2022/042022 2021-11-29 2022-11-11 Pompe centrifuge, dispositif à pompe centrifuge, et automobile de lutte contre l'incendie WO2023095638A1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
ATA9258/2022A AT526707A5 (de) 2021-11-29 2022-11-11 Kreiselpumpe, Kreiselpumpenvorrichtung und Feuerwehrfahrzeug
CN202280058907.6A CN117881899A (zh) 2021-11-29 2022-11-11 离心泵、离心泵装置以及消防车

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2021193366 2021-11-29
JP2021-193366 2021-11-29

Publications (1)

Publication Number Publication Date
WO2023095638A1 true WO2023095638A1 (fr) 2023-06-01

Family

ID=86539519

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/JP2022/042022 WO2023095638A1 (fr) 2021-11-29 2022-11-11 Pompe centrifuge, dispositif à pompe centrifuge, et automobile de lutte contre l'incendie

Country Status (3)

Country Link
CN (1) CN117881899A (fr)
AT (1) AT526707A5 (fr)
WO (1) WO2023095638A1 (fr)

Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5424103U (fr) * 1977-07-21 1979-02-16
JPS62179394U (fr) * 1986-05-06 1987-11-14
JP2000154796A (ja) * 1998-11-19 2000-06-06 Mitsubishi Heavy Ind Ltd 羽根車
JP2004092527A (ja) * 2002-08-30 2004-03-25 Ebara Corp 自吸水ポンプ
JP2004162591A (ja) * 2002-11-12 2004-06-10 Ebara Corp 自吸水ポンプ
FR2974866A1 (fr) * 2011-05-03 2012-11-09 Francois Gerlier Pompe de circulation d'electrolyte pour engin marin
JP2017070720A (ja) * 2015-10-09 2017-04-13 株式会社モリタホールディングス ポンプ装置及びポンプ装置を搭載した作業車
WO2017138472A1 (fr) * 2016-02-10 2017-08-17 株式会社荏原製作所 Carter d'aspiration pour pompe submersible à multiples étages, et pompe submersible à multiples étages

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
IT8024009A0 (it) * 1979-09-03 1980-08-05 Klein Schanzlin & Becker Ag Dispositivo per migliorare il comportamento di cavitazione di pompe centrifughe.
US20110027071A1 (en) * 2009-08-03 2011-02-03 Ebara International Corporation Multi-stage inducer for centrifugal pumps
US9562502B2 (en) * 2014-10-06 2017-02-07 Hamilton Sundstrand Corporation Impeller for engine-mounted boost stage fuel pump
US20190345955A1 (en) * 2018-05-10 2019-11-14 Mp Pumps Inc. Impeller pump

Patent Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5424103U (fr) * 1977-07-21 1979-02-16
JPS62179394U (fr) * 1986-05-06 1987-11-14
JP2000154796A (ja) * 1998-11-19 2000-06-06 Mitsubishi Heavy Ind Ltd 羽根車
JP2004092527A (ja) * 2002-08-30 2004-03-25 Ebara Corp 自吸水ポンプ
JP2004162591A (ja) * 2002-11-12 2004-06-10 Ebara Corp 自吸水ポンプ
FR2974866A1 (fr) * 2011-05-03 2012-11-09 Francois Gerlier Pompe de circulation d'electrolyte pour engin marin
JP2017070720A (ja) * 2015-10-09 2017-04-13 株式会社モリタホールディングス ポンプ装置及びポンプ装置を搭載した作業車
WO2017138472A1 (fr) * 2016-02-10 2017-08-17 株式会社荏原製作所 Carter d'aspiration pour pompe submersible à multiples étages, et pompe submersible à multiples étages

Also Published As

Publication number Publication date
CN117881899A (zh) 2024-04-12
AT526707A5 (de) 2024-04-15

Similar Documents

Publication Publication Date Title
US9771856B2 (en) Centrifugal compressor
US7021890B2 (en) Turbo pump
JP5479316B2 (ja) 遠心圧縮機のスクロール構造
JP5879103B2 (ja) 遠心式流体機械
JP5762641B2 (ja) 斜流タービン
JP7082948B2 (ja) 遠心圧縮機、ターボチャージャ
JP5649055B2 (ja) バーレル型多段ポンプ
US5108257A (en) Impeller for turbo pump for water jet propulsion machinery, and turbo pump including same impeller
JP6730917B2 (ja) 遠心圧縮機及びターボチャージャ
JP2006002689A (ja) 送風機
JP6064003B2 (ja) 遠心式流体機械
WO2023095638A1 (fr) Pompe centrifuge, dispositif à pompe centrifuge, et automobile de lutte contre l'incendie
JP3899829B2 (ja) ポンプ
JP6949227B2 (ja) 遠心圧縮機及びターボチャージャ
JP2020186649A (ja) 遠心圧縮機のインペラ、遠心圧縮機及びターボチャージャ
JPH10331794A (ja) 遠心圧縮機
WO1999036701A1 (fr) Turbomachines centrifuges
JP6839040B2 (ja) 遠心式流体機械
JP7386333B2 (ja) インペラ、及び遠心圧縮機
JP7452708B2 (ja) 遠心圧縮機および過給機
JP7123029B2 (ja) 遠心圧縮機
JP2021124046A (ja) 遠心圧縮機のディフューザ構造及び遠心圧縮機
JP2022189406A (ja) ポンプ装置及び整流部材
CN115698516A (zh) 蜗壳和离心压缩机
JP2024002113A (ja) 遠心圧縮機のインペラ、遠心圧縮機及びターボチャージャ

Legal Events

Date Code Title Description
121 Ep: the epo has been informed by wipo that ep was designated in this application

Ref document number: 22898422

Country of ref document: EP

Kind code of ref document: A1

WWE Wipo information: entry into national phase

Ref document number: 2023563617

Country of ref document: JP

WWE Wipo information: entry into national phase

Ref document number: 202280058907.6

Country of ref document: CN

WWE Wipo information: entry into national phase

Ref document number: A 9258/2022

Country of ref document: AT