WO2015001830A1 - 水中ポンプ用ポンプ羽根及びこれを備えた水中ポンプ - Google Patents

水中ポンプ用ポンプ羽根及びこれを備えた水中ポンプ Download PDF

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Publication number
WO2015001830A1
WO2015001830A1 PCT/JP2014/060657 JP2014060657W WO2015001830A1 WO 2015001830 A1 WO2015001830 A1 WO 2015001830A1 JP 2014060657 W JP2014060657 W JP 2014060657W WO 2015001830 A1 WO2015001830 A1 WO 2015001830A1
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WO
WIPO (PCT)
Prior art keywords
pump
pump blade
flow path
suction port
flow paths
Prior art date
Application number
PCT/JP2014/060657
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English (en)
French (fr)
Japanese (ja)
Inventor
川井　政人
浩美 坂頂
真志 大渕
博 打田
美帆 磯野
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
Family has litigation
First worldwide family litigation filed litigation Critical https://patents.darts-ip.com/?family=52143424&utm_source=google_patent&utm_medium=platform_link&utm_campaign=public_patent_search&patent=WO2015001830(A1) "Global patent litigation dataset” by Darts-ip is licensed under a Creative Commons Attribution 4.0 International License.
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 CN201480002515.3A priority Critical patent/CN104662302B/zh
Priority to EP14819908.6A priority patent/EP2930367B1/en
Priority to US14/439,879 priority patent/US20160108927A1/en
Priority to BR112015009797-9A priority patent/BR112015009797B1/pt
Priority to DK14819908.6T priority patent/DK2930367T3/da
Publication of WO2015001830A1 publication Critical patent/WO2015001830A1/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
    • F04D7/00—Pumps adapted for handling specific fluids, e.g. by selection of specific materials for pumps or pump parts
    • F04D7/02—Pumps adapted for handling specific fluids, e.g. by selection of specific materials for pumps or pump parts of centrifugal type
    • F04D7/04—Pumps adapted for handling specific fluids, e.g. by selection of specific materials for pumps or pump parts of centrifugal type the fluids being viscous or non-homogenous
    • 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
    • F04D29/2238—Special flow patterns
    • F04D29/225—Channel wheels, e.g. one blade or one flow channel
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D13/00—Pumping installations or systems
    • F04D13/02—Units comprising pumps and their driving means
    • 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
    • F04D29/2238—Special flow patterns
    • F04D29/2255—Special flow patterns flow-channels with a special cross-section contour, e.g. ejecting, throttling or diffusing effect
    • 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
    • F04D29/426—Casings; Connections of working fluid for radial or helico-centrifugal pumps 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
    • F04D29/00—Details, component parts, or accessories
    • F04D29/66—Combating cavitation, whirls, noise, vibration or the like; Balancing
    • F04D29/669—Combating cavitation, whirls, noise, vibration or the like; Balancing especially adapted for liquid pumps

Definitions

  • the present invention relates to a pump blade for a submersible pump, and more particularly to a pump blade for a submersible pump used for sewage waste and a submersible pump equipped with the same.
  • the pump blade 111 has a suction port 129 formed at one end and a discharge port 134 formed laterally on the other end side, and a spiral flow path 135 that connects the suction port 129 and the discharge port 134 is defined inside.
  • This is a substantially cylindrical pump blade 111 formed.
  • a flange portion 140 that protrudes outward along the outer peripheral surface from the suction port side portion of the outer peripheral surface of the pump blade 111 from the suction port side and partitions the suction port side and the discharge port side is provided. Yes.
  • the pump blade 111 is accommodated in a pump casing 112 and connected to a sealed submersible motor 113 for rotationally driving the pump blade 111.
  • the underwater motor 113 includes a motor 116 including a stator 114 and a rotor 115, and a motor casing 117 that covers the motor 116.
  • a drive shaft 118 extending in the vertical direction is provided at the center of the rotor 115. The upper end portion of the drive shaft 118 and the middle portion on the slightly lower side are rotatably supported by bearings 119 and 120, respectively.
  • the pump blade 111 is connected to the lower end portion of the drive shaft 118.
  • a pump chamber 126 defined by an inner wall 125 having a semicircular cross section is formed in the pump casing 112.
  • the discharge part 138 of the pump blade 111 is accommodated in the pump chamber 126.
  • a suction portion 121 that protrudes downward is formed in the lower portion of the pump casing 112.
  • a suction port 122 that opens downward is formed in the suction part 121.
  • the discharge part 123 is formed with a discharge port 124 that opens to the side.
  • the pump blade 111 is provided with a suction portion 127 and a discharge portion 128 in order from the lower side to the upper side in the axial direction.
  • the suction part 127 and the discharge part 128 are both formed in a substantially cylindrical shape, and the discharge part 128 is configured to have a larger diameter than the suction part 127.
  • the discharge part 128 and the suction part 127 are partitioned by a flange part 140 protruding outward from the outer peripheral surface of the pump blade 11.
  • a suction port 129 that opens downward is provided at the lower end of the suction portion 127 of the pump blade 111.
  • the upper side of the discharge part 128 is covered with an upper end wall. That is, the upper side of the pump blade 111 is sealed by the upper end wall.
  • a hole into which the tip of the drive shaft 118 is inserted is formed at the center of the upper end wall, and a peripheral portion of the hole constitutes an attachment portion 131 for attaching the drive shaft 118.
  • Reference numeral 137 represents a secondary flow path
  • reference numeral 138 represents a secondary blade.
  • the number of flow paths from the suction port 129 to the discharge port 134 is one. That is, sewage filth is sucked from the suction port 129 that is coaxial with the drive shaft 118 and opens downward, and the sewage filth is discharged from the discharge port 134 through one spiral channel. Yes.
  • the part in which the spiral flow path is formed is a space, there is no weight.
  • wing 111 has weight. For this reason, with respect to the axis (rotation center) of the drive shaft 118, the weight of the pump blade 111 is greatly deviated along the circumferential direction. When such a pump blade 111 rotates, the deviation of the weight of the fluid with respect to the rotation center also increases, and a radial load is likely to be generated.
  • the above-mentioned dynamic balance is defined as a deviation of the center of gravity and the center of moment with respect to the rotation axis when the impeller is rotated in the air.
  • the dynamic balance can be removed by the correction work such as the above-described meat removal.
  • the fluid balance refers to the balance when the fluid is flowing in the flow path with the rotation of the pump blade. Even if the above-mentioned dynamic balance is optimal (weight unbalance is 0), when the pump blade is rotated in water, the water (sewage waste) region in the pump blade is biased with respect to the rotation axis. For this reason, fluid imbalance arises and force (this is called radial load) acts on a pump blade through wall pressure.
  • the present invention has been made in view of the above problems, and in the first means, a substantially cylindrical main body portion, a suction port provided at the center of the lower end surface of the main body portion, and an opening on the side surface of the main body portion
  • a non-clog type pump blade for a submersible pump comprising a discharge port and a flow channel communicating from the suction port to the discharge port inside the main body, and there are a plurality of flow channels.
  • the configuration is such that the size, shape and position of the flow path are set so as to reduce the fluid imbalance with respect to the rotation axis.
  • the second means adopts a configuration in which the number of flow paths is two or more.
  • the flow path has a configuration in which the cross-sectional area changes between the suction port and the discharge port.
  • the pump blade according to the present invention when sewage filth is separated from the surface of the flow path near the discharge port, the sewage filth cannot be sucked from the suction port. For this reason, a cross-sectional area changes with places so that the pressure more than predetermined may be maintained.
  • the flow path has a configuration in which the cross-sectional shape changes between the suction port and the discharge port.
  • the cross-sectional shape of the flow path is changed from a circular shape to a substantially rectangular shape or an elliptical shape from the suction port toward the discharge port.
  • the suction port is circular, and the upstream portion of the flow path is also circular, whereas the outer peripheral surface of the pump blade is close to the shape of the outer peripheral surface of the cylinder. For this reason, in order to ensure a constant cross-sectional area, it is necessary to change the cross-sectional shape near the discharge port.
  • the flow path has a configuration in which the inner wall surface is formed by a continuous curved surface.
  • the inner wall in the vicinity of the branch portion of at least two flow paths has a different surface roughness.
  • a long fibrous foreign matter may flow in two flow paths at a branch portion near the suction port.
  • the surface roughness is different between the flow paths, the frictional resistance on the flow path side having a smooth surface is low, and there is a high possibility that foreign matter flows on that side.
  • all the flow paths have the same size and shape and are arranged at equiangular intervals with respect to the rotation axis.
  • a submersible pump comprising the pump blade according to any one of means 1 to 8, a pump casing for housing the pump blade, and a motor for driving the pump blade. Adopted.
  • the following effects can be obtained as an example. 1. Since the fluid balance of the pump blade can be taken with respect to the rotation axis, the average value of the radial load during operation can be reduced. 2. With the reduction of the radial load described above, noise and vibration during operation are reduced. Moreover, it is possible to change a bearing to a thing with a small capacity
  • the suction flow path in the vicinity of the suction port is a straight flow path that coincides with the rotation axis, so that the flow path length at the inlet portion is shortened, the flow smoothly flows in, loss is reduced, and hydraulic efficiency is improved. Improvement can be expected.
  • FIG. 1 It is a figure which shows one flow path, and is the perspective view which showed the shape of the flow path. It is a figure which shows one flow path, and is a top view. It is a figure which shows the two flow paths used for the pump blade
  • FIG. 4 is a plan view of the pump blade disclosed in FIG. 3.
  • FIG. 4 is a side view of the pump blade disclosed in FIG. 3.
  • FIG. 4 is a bottom view (suction port side) of the pump blade disclosed in FIG. 3.
  • FIG. 5 is a cross-sectional view of a pump blade desired to be disclosed in FIG. 4, and is a cross-sectional view taken along line 5A-5A in FIG.
  • FIG. 5 is a cross-sectional view of a pump blade desired to be disclosed in FIG. 4, and is a cross-sectional view taken along line 5B-5B in FIG. 4 (B).
  • the pump blade according to the present embodiment includes a plurality of flow paths that allow the suction port coaxial with the rotation axis to communicate with the discharge port on the outer peripheral portion, and the flow paths are arranged in a logical sum at equal angular intervals with respect to the rotation axis. .
  • the number of flow paths is not particularly limited, but those shown in FIGS. 3 to 5 are embodiments with two flow paths, and those shown in FIGS. 6 to 8 are those with three flow paths. It is an embodiment.
  • the flow path is formed in a curved shape between the suction port and the discharge port. This pump blade is manufactured by casting as an example.
  • FIG. 1 (A) is an image produced by computer graphics showing the flow path 3 used in the pump blade.
  • the flow path is coaxial with the rotation axis C in the vicinity of the suction port 5. That is, the central axis of the flow path 3 in the vicinity of the suction port 5 is parallel to and coincides with the rotation axis C.
  • the central axis of the flow path 3 goes downward in the radial direction with respect to the rotation axis C while proceeding downward.
  • the transition portion from the rotational axis direction to the radially outer side is formed by a continuous curve.
  • the central axis of the flow path 3 is also directed in the circumferential direction with respect to the rotational axis C while being directed radially outward. For this reason, the center axis of the flow path 3 goes outward in a spiral shape by combining the radially outer component and the circumferential component.
  • the cross-sectional shape of the flow path 3 is a perfect circle in the vicinity of the suction port 5, but is a rectangle in the vicinity of the discharge port 7. For this reason, the transition region from the suction port 5 toward the discharge port 7 continuously changes so that the circle gradually becomes a rectangle.
  • the corner portion is not a complete right-angle surface, but is formed by a curved surface with a small radius of curvature. This is to prevent foreign matters from clogging the corners.
  • FIG. 1A the theoretical shape of the flow path 3 is shown, but when actually applied to the pump blade, the outer edge of the pump blade is circular with the rotation axis C as the center. Specifically, the ellipse shown in FIG. 1A defines the outer edge of the pump blade. For this reason, the actual flow path 3 formed in the pump blade has such a shape that the discharge port 7 is formed over a wide angular range, as shown in FIG.
  • the above is the shape of the flow path 3 used for the pump blades, but this only explains the case where there is only one flow path 3.
  • this embodiment is characterized by combining two flow paths, and a specific example thereof will be described.
  • FIG. 2A two flow paths 13A and 13B are provided, and these flow paths 13A and 13B are configured by taking a logical sum with reference to the rotation axis C (suction port). .
  • Each flow path 13A, 13B has completely the same size and shape, and is arranged at a point-symmetrical position with respect to the central axis C.
  • the flow path 3 of FIG. 1 is rotationally copied and arranged at equiangular intervals. Therefore, as shown in FIG. 2 (B), the regions where the flow paths 13A and 13B are directed radially outward from the suction port 15 extend in directions (opposite directions) that are 180 ° apart from each other.
  • the logical sum means that the two flow paths are simply combined with the suction port in common.
  • FIG. 2 (B) is a diagram showing the actual flow paths 13A and 13B by the outer edges (indicated by dotted lines) of the pump blades, as in FIG. 1 (B). As shown in this figure, each of the flow paths 13A and 13B is completely point-symmetric with respect to the rotation axis C, and forms a generally S-shaped flow path as a whole. In the vicinity of the outer edge of the pump blade, discharge ports 17A and 17B are formed over a wide angular range, as in the example of FIG.
  • FIG. 3 is a diagram in which the pump blade 11 according to the present embodiment is produced by computer graphics.
  • FIG. 3 (A) is a view seen obliquely from the suction port 15 side
  • FIG. 3 (B) is a view seen from the side.
  • the flow paths formed inside the pump blade 11 shown in this figure are the flow paths 13A and 13B shown in FIG.
  • the cross-sectional shape of the flow path is close to a circle on the right side (upstream side) of the rotation axis C, and forms a part of a rectangle on the left side (downstream side) of the rotation axis. It has become a shape.
  • FIG. 4 shows the pump blade 11 of this embodiment
  • FIG. 4 (A) is a top view
  • FIG. 4 (B) is a side view
  • FIG. 4 (C) is a bottom view.
  • a cylindrical hub 14 is formed in the region of the central axis C
  • a drive shaft (not shown) of a drive motor is provided on the hub 14. It is supposed to be inserted.
  • the pump blade 11 rotates at a rotational speed of about 1500 rpm, for example. However, if the efficiency is improved, it can be rotated at a rotational speed lower than 1500 rpm or higher.
  • FIG. 5A is a cross-sectional view taken along line 5A-5A in FIG. 4B.
  • the pump blade 11 is formed with a suction port 15 that opens on one side of the central axis C, and sewage filth is sucked as the pump blade 11 rotates. .
  • the sewage filth is transferred from the suction port 15 to the outside in the circumferential direction along the flow paths 13A and 13B, and finally discharged from the discharge ports 17A and 17B.
  • an opening is also formed on the other end side of the central axis C. However, since the drive shaft is inserted as described above, sewage filth does not leak from this opening.
  • FIG. 5B is a cross-sectional view taken along line 5B-5B in FIG. 4B.
  • the flow paths 13A and 13B connected from the suction port 15 extend outward in the radial direction in a spiral shape, and form discharge ports 17A and 17B at the outer edge portion of the pump blade 11.
  • the part other than the flow path is a wall part constituting the pump blade 11.
  • the discharge ports 17A and 17B of the present embodiment are formed in an angle range of about 180 ° with respect to the central axis C. This is based on the basic idea that there are two flow paths 13A and 13B and that the discharge ports 17A and 17B are formed over as wide an angular range as possible to improve efficiency.
  • the pump casing 16 is also shown for convenience of explanation. The relationship between the pump blade 11 and the pump casing 16 will be described later.
  • the suction port 15 is cylindrical and opens so as to be coaxial with the rotation axis C. For this reason, one suction port 15 which is substantially common is obtained by logical sum.
  • the suction port 15 is arranged to open downward.
  • the inner diameter of the suction port 15 is set based on the size of the solid matter contained in the sewage filth handled by the pump blade 11.
  • the cross-sectional area gradually decreases from the branch portion toward the downstream side. This is because, if the cross-sectional areas of the flow paths 13A and 13B after branching are equal to the cross-sectional area of the suction port 15, the total area is doubled and the pressure of the sewage filth is reduced. This is because a sewage detachment phenomenon from the inner surfaces of the paths 13A and 13B occurs. If such a peeling phenomenon occurs, it is conceivable that the efficiency of the pump is lowered, and in some cases, the sewage filth cannot be sucked from the suction port 15. For this reason, the cross-sectional area of the flow paths 13A and 13B after branching is made smaller than the cross-sectional area of the suction port 15 as described above.
  • the reduction ratio of the cross-sectional areas of the flow paths 13A and 13B after branching is variously changed according to the properties of the sewage filth to be handled and parameters such as the number of rotations of the pump blade 11. For example, when the viscosity of sewage filth is high, the peeling phenomenon is unlikely to occur, and therefore the reduction rate of the cross-sectional area may be reduced. Further, when the rotational speed of the pump blade 11 is high, a peeling phenomenon is likely to occur, so it is desirable to increase the reduction ratio of the cross-sectional area. Regarding the specific reduction ratio of the cross-sectional area, for example, when the cross-sectional area of the suction port 15 is 1, the cross-sectional area of the flow path after branching is about 0.55 (when there are two flow paths). .
  • the inner wall surfaces of the flow paths 13A and 13B in the vicinity of the branch portion are formed so that the surface roughness is different from each other.
  • the fibrous object can be smoothly flowed into the one flow path 13A or 13B. That is, the inner surface of one channel 13A is smoothed, and the inner surface of the other channel 13B is rough (for example, as cast). In such a case, the frictional resistance of the fibrous object is small on the smooth inner surface, and conversely, the friction coefficient is increased on the rough inner surface.
  • Such a friction coefficient imbalance causes the fibrous object to flow toward the flow path having a smooth inner surface.
  • the cross-sectional areas of the flow paths 13A and 13B are defined so that sewage filth is not separated from the inner surfaces of the flow paths 13A and 13B in the vicinity of the discharge ports 17A and 17B.
  • the cross-sectional areas of the flow paths 13A and 13B may be gradually changed from the suction port 15 toward the discharge ports 17A and 17B.
  • the predetermined section has a constant cross-sectional area and the other sections have different sizes. It may have a constant cross-sectional area.
  • the cross-sectional shape of the flow paths 13A and 13B of the present embodiment changes from a circular shape to a rectangular shape between the suction port 15 and the discharge ports 17A and 17B.
  • these cross-sectional shapes are merely examples.
  • the shape may be circular ⁇ transition region ⁇ elliptical in order from the suction port 15 to the discharge ports 17A and 17B, or a combination of circular ⁇ transition region ⁇ elliptical ⁇ transition region ⁇ rectangle.
  • the rectangle of this embodiment is a square, you may make it a rectangular cross section.
  • all the inner wall surfaces of the flow paths 13A and 13B are formed as continuous curved surfaces. This is to prevent clogging of foreign matters in the flow paths 13A and 13B.
  • the cross-sectional shapes of the flow paths 13A and 13B are rectangular in the vicinity of the discharge ports 17A and 17B. However, the corners of the cross section are not completely right angles but connected by a continuous curved surface.
  • the shape of the longitudinal axis of the flow paths 13A and 13B (the line connecting the cross-sectional centers of the discharge ports 17A and 17B from the suction port 15) is also continuous. For this reason, it is prevented that it catches in flow path 13A, 13B in the process in which sewage filth flows.
  • FIG. 6 and 7 are diagrams for explaining the pump blade 21 according to the second embodiment, which includes three flow paths.
  • FIG. 6A corresponds to FIG. 2A of the first embodiment
  • FIG. 6B corresponds to FIG. 2B
  • FIG. 7 corresponds to FIG.
  • FIG. 6 is a diagram showing a state in which the three flow paths 23A, 23B, and 23C are arranged at equiangular intervals with the suction port 25 as the center.
  • each of the flow paths 23A, 23B, and 23C has completely the same size and shape, and the rotational path C of FIG. They are arranged at angular intervals. Therefore, as shown in FIG. 6B, the regions where the flow paths 23A, 23B, and 23C are directed radially outward from the suction port 25 extend in directions that are 120 ° apart from each other.
  • FIG. 6B is a diagram showing the actual flow paths 23A, 23B, and 23C by the outer edges (indicated by dotted lines) of the pump blades 23, as in FIG. 2B.
  • discharge ports 27A, 27B, and 27C are formed over a wide angle range (about 120 °) as in the example of FIG.
  • FIG. 7 is a cross-sectional view showing a state where pump blades are housed in the actual pump casing 26.
  • sewage filth is discharged from the three flow paths 23A, 23B, and 23C three times for each rotation. For this reason, when it is assumed that the discharge flow rate is the same, the pressure fluctuation at the time of discharge is suppressed to be lower than that of the pump blade 11 of the first embodiment having two flow paths.
  • FIG. 9 is a cross-sectional view of the submersible pump 60 including the above-described pump blade 11 according to the present embodiment.
  • the pump blade 11 is accommodated in a pump casing 62 and is connected to a sealed submersible motor 63 for rotationally driving the pump blade 11.
  • the submersible motor 63 includes a motor 66 including a stator 64 and a rotor 65, and a motor casing 67 that covers the motor 66.
  • a drive shaft 68 extending in the vertical direction is provided at the center of the rotor 65.
  • the upper end portion of the drive shaft 68 and the middle portion on the slightly lower side are rotatably supported by bearings 69 and 70, respectively.
  • the pump blade 11 is connected to the lower end portion of the drive shaft 68.
  • a pump chamber 76 defined by an inner wall 75 having a semicircular cross section is formed inside the pump casing 62.
  • the discharge part 88 of the pump blade 11 is accommodated in the pump chamber 76.
  • a suction portion 71 protruding downward is formed at the lower portion of the pump casing 62.
  • the suction portion 71 is formed with a suction port 72 that opens downward.
  • a discharge portion 73 projecting sideways is formed on the side of the pump casing 62.
  • the discharge portion 73 is formed with a discharge port 74 that opens to the side.
  • the pump blade according to the present invention can be used particularly for a submersible pump for sewage waste.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
PCT/JP2014/060657 2013-07-05 2014-04-15 水中ポンプ用ポンプ羽根及びこれを備えた水中ポンプ WO2015001830A1 (ja)

Priority Applications (5)

Application Number Priority Date Filing Date Title
CN201480002515.3A CN104662302B (zh) 2013-07-05 2014-04-15 潜水泵用泵叶片以及具有该泵叶片的潜水泵
EP14819908.6A EP2930367B1 (en) 2013-07-05 2014-04-15 Pump blade for submerged pump and submerged pump having same
US14/439,879 US20160108927A1 (en) 2013-07-05 2014-04-15 Pump impeller for submerged pump and submerged pump including same
BR112015009797-9A BR112015009797B1 (pt) 2013-07-05 2014-04-15 Impulsor de bomba para bomba submersa e bomba submersa, incluindo a mesma
DK14819908.6T DK2930367T3 (da) 2013-07-05 2014-04-15 Pumpeblade til nedsænket pumpe og nedsænket pumpe havende samme

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2013-141415 2013-07-05
JP2013141415A JP6351216B2 (ja) 2013-07-05 2013-07-05 水中ポンプ用ポンプ羽根及びこれを備えた水中ポンプ

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WO2015001830A1 true WO2015001830A1 (ja) 2015-01-08

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PCT/JP2014/060657 WO2015001830A1 (ja) 2013-07-05 2014-04-15 水中ポンプ用ポンプ羽根及びこれを備えた水中ポンプ

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US (1) US20160108927A1 (pt)
EP (1) EP2930367B1 (pt)
JP (1) JP6351216B2 (pt)
CN (1) CN104662302B (pt)
BR (1) BR112015009797B1 (pt)
DK (1) DK2930367T3 (pt)
WO (1) WO2015001830A1 (pt)

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EP2930367B1 (en) 2013-07-05 2020-05-27 Ebara Corporation Pump blade for submerged pump and submerged pump having same

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CN105736391B (zh) * 2016-02-18 2018-11-02 广州道动新能源有限公司 一种风能驱动的灌溉系统
KR101816766B1 (ko) 2016-09-02 2018-01-09 이신구 에너지 절감형 펌프
KR101712381B1 (ko) * 2016-11-21 2017-03-16 고일영 맨홀펌프용 임펠러
MX2019010836A (es) * 2019-09-12 2020-10-28 Antonio Ochoa Barraza Impulsor de doble turbina interna.
RU2735971C1 (ru) * 2020-02-25 2020-11-11 Игорь Олегович Стасюк Рабочее колесо ступени лопастного насоса

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BR112015009797B1 (pt) 2022-03-15
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EP2930367A1 (en) 2015-10-14
JP6351216B2 (ja) 2018-07-04
DK2930367T3 (da) 2020-06-29
JP2015014251A (ja) 2015-01-22
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US20160108927A1 (en) 2016-04-21
BR112015009797A2 (pt) 2017-07-11

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