US20160108927A1 - Pump impeller for submerged pump and submerged pump including same - Google Patents

Pump impeller for submerged pump and submerged pump including same Download PDF

Info

Publication number
US20160108927A1
US20160108927A1 US14/439,879 US201414439879A US2016108927A1 US 20160108927 A1 US20160108927 A1 US 20160108927A1 US 201414439879 A US201414439879 A US 201414439879A US 2016108927 A1 US2016108927 A1 US 2016108927A1
Authority
US
United States
Prior art keywords
pump impeller
pump
flow channels
flow channel
intake port
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
Application number
US14/439,879
Other languages
English (en)
Inventor
Masahito Kawai
Hiromi Sakacho
Masashi Obuchi
Hiroshi Uchida
Miho ISONO
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.)
Ebara Corp
Original Assignee
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
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=US20160108927(A1) "Global patent litigation dataset” by Darts-ip is licensed under a Creative Commons Attribution 4.0 International License.
Application filed by Ebara Corp filed Critical Ebara Corp
Assigned to EBARA CORPORATION reassignment EBARA CORPORATION ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: ISONO, Miho, KAWAI, MASAHITO, OBUCHI, MASASHI, SAKACHO, HIROMI, UCHIDA, HIROSHI
Publication of US20160108927A1 publication Critical patent/US20160108927A1/en
Abandoned legal-status Critical Current

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
    • 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 impeller for a submerged pump, and in particular to a pump impeller for a submerged pump for sewage and a submerged pump provided with the impeller.
  • a pump impeller 111 as illustrated in FIG. 9 is used within the submerged pump (see Patent Literature 1).
  • the pump impeller 111 is generally in a cylindrical shape, which includes an intake port 129 formed at one end and a discharge port 134 formed laterally on the side of the other end, and a spiral flow channel 135 partitioned and formed therein, connecting the intake port 129 with the discharge port 134 .
  • the pump impeller 111 further includes a flange portion 140 that protrudes outward along the circumferential surface of the pump impeller 111 from a portion closer to the intake port than the discharge port 134 on the circumferential surface and separates the intake port side from the discharge port side.
  • the pump impeller 111 is contained in a pump casing 112 and connected to a closed-type submerged motor 113 for rotatably driving the pump impeller 111 .
  • the submerged motor 113 includes a motor 116 having a stator 114 and a rotor 115 and a motor casing 117 that covers the motor 116 .
  • a driving shaft 118 extending vertically is provided at the center portion of the rotor 115 .
  • the driving shaft 118 is rotatably supported by bearings 119 and 120 at the upper end portion and an intermediate portion on the lower side, respectively.
  • the pump impeller 111 is then connected to the lower end portion of the driving shaft 118 .
  • a pump chamber 126 which is partitioned by an inner wall 125 that is recessed in a semicircular shape in its cross section, is formed within the pump casing 112 .
  • a discharge portion 138 of the pump impeller 111 is contained in the pump chamber 126 .
  • An intake portion 121 that protrudes downward is formed in the lower portion of the pump casing 112 .
  • An intake port 122 that is open downward is formed in the intake portion 121 .
  • a discharge portion 123 that protrudes laterally is formed on the side portion of the pump casing 112 .
  • the discharge portion 123 includes a discharge port 124 formed therein, which is open laterally.
  • the pump impeller 111 is provided with an intake portion 127 and a discharge portion 128 axially from the lower side toward the upper side in this order.
  • the intake portion 127 and the discharge portion 128 are both formed generally in a cylindrical shape, and the discharge portion 128 is constructed to have a diameter larger than the intake portion 127 .
  • the discharge portion 128 is separated from the intake portion 127 by the flange portion 140 that protrudes outward from the circumferential surface of the pump impeller 11 .
  • An intake port 129 that is open downward is formed at the lower end of the intake portion 127 of the pump impeller 111 .
  • the upper side of the discharge portion 128 is covered by an upper end wall. In other words, the upper side of the pump impeller 111 is hermetically closed by the upper end wall.
  • a hole is provided at the center portion of the upper end wall for inserting a distal end of the driving shaft 118 , and a periphery of the hole constitutes a mounting portion 131 for mounting the driving shaft 118 .
  • the reference numeral 137 denotes a secondary flow channel and the reference numeral 138 denotes a secondary blade.
  • Patent Literature 1 Japanese Patent No. 4713066
  • the pump impeller 111 is adapted to take in sewage from the intake port 129 that is open downward in coaxial with the driving shaft 118 , and the sewage is drained from the discharge port 134 through the one spiral flow channel.
  • the area where the spiral flow channel is formed is weightless because it is hollow space.
  • the area forming the wall of the pump impeller 111 has weight. For this reason, the weight of the pump impeller 111 is significantly eccentrically distributed in the circumference direction with respect to the axis (center of rotation) of the driving shaft 118 . When such pump impeller 111 rotates, the deviation of the weight of fluid also increases with respect to the center of rotation, which is likely to cause a radial load.
  • the above-mentioned “dynamic balance” is defined herein as displacement of the center of gravity and the center of moment with respect to the axis of rotation when an impeller is rotated in the atmosphere.
  • the dynamic balance can be removed by a correction such as thinning of the wall as described above.
  • the fluid balance refers to balance in the case where a fluid is flowing in a channel while a pump impeller is rotating. Even if the dynamic balance is optimized (zero weight unbalance), the area of water (sewage) in the pump impeller is eccentric with respect to the axis of rotation when the pump impeller is rotated under water. This causes fluid unbalance and a force (which is referred to as a radial load) is applied to the pump impeller via the wall pressure.
  • a large radial load may cause vibration, and thus efforts have been made to cancel the load, such as by applying a weight.
  • a multi-channel pump impeller such as that in the present invention can significantly reduce the radial load because the mass distribution of the water area is less likely to be nonaxisymmetric as compared to a single-channel pump impeller.
  • the present invention which has been made in view of the above problem, provides in a first aspect a pump impeller for a non-clogging submerged pump including a generally cylindrical body, an intake port provided in a center of a lower end surface of the body, a discharge port that is open in a side surface of the body, and a flow channel passing from the intake port to the discharge port within the body.
  • the flow channel includes a plurality of flow channels, and the flow channels have their size, shape, and position defined such that fluid unbalance is reduced with respect to an axis of rotation.
  • sewage taken in from the intake port is divided and flows into each of the flow channels.
  • fluid unbalance is less likely to occur with respect to the axis of rotation because the flow channels are designed to reduce the fluid unbalance, and thus the occurrence of radial load associated with rotation of the pump impeller can significantly be suppressed.
  • the flow channel includes two or more flow channels. According to the configuration, sewage is drained more than once per revolution of the pump impeller, and thus pressure variation during drainage can be suppressed.
  • a cross-sectional area of the flow channel varies between the intake port and the discharge port.
  • sewage when sewage separates from a surface of the flow channel near the discharge port, sewage may be prevented from being taken in from the intake port. Accordingly, the varying cross-sectional area is provided in some positions in order to maintain the pressure above a predetermined level.
  • a cross-sectional shape of the flow channel varies between the intake port and the discharge port. Furthermore, in a fifth aspect, the cross-sectional shape of the flow channel changes from circular to generally rectangular or elliptic from the intake port toward the discharge port.
  • the intake port is circular and an upstream portion of the flow channel is also circular; while the circumferential surface of the pump impeller has a shape similar to that of a circumferential surface of a cylinder. Accordingly, the cross-sectional shape needs to be changed near the discharge port in order to secure a constant cross-sectional area.
  • an inner wall surface of the flow channel is formed of a continuous curved surface. According to the configuration, foreign matters in sewage flow smoothly in the flow channel so that the occurrence of clogging or the like due to the foreign matters can be prevented.
  • inner walls close to a junction of at least two of the flow channels have a surface roughness different from each other.
  • elongated fibrous foreign matters may be divided and flow into two flow channels at a junction close to the intake port.
  • the frictional resistance is lower on the side of a flow channel having a smoother surface, so that the foreign matters are likely to flow in the side of the flow channel.
  • all of the flow channels have the same size and shape, and are disposed at an equal angular interval with respect to the axis of rotation. According to the configuration, sewage taken in from the intake port is divided and flows into each of the flow channels. At this time, since the flow channels have the same size and shape, and are disposed in positions located at an equal angular interval with respect to the axis of rotation, no weight unbalance with respect to the axis of rotation occurs, and thus the occurrence of radial load associated with rotation of the pump impeller can be minimized.
  • a submerged pump is characterized by including a pump impeller according to any one of the first to eighth aspects, a pump casing that contains the pump impeller; and a motor that drives the pump impeller. According to the configuration, a pump having a good fluid balance can be realized when assembled and operated as a pump, without problems such as noise and vibration.
  • An average radial load can be reduced in operation because the fluid balance of the pump impeller can be achieved with respect to the axis of rotation.
  • the bearing can be replaced with one that has a smaller capacity, and even when a conventional bearing is still used, the rated number of revolution of the pump impeller can be increased.
  • FIG. 1(A) illustrates one flow channel, and is a perspective view illustrating the shape of the flow channel.
  • FIG. 1(B) illustrates one flow channel, and is a plan view.
  • FIG. 2(A) illustrates two flow channels used in a pump impeller according to an embodiment of the preset invention, and is a perspective view illustrating the shape of the flow channels.
  • FIG. 2(B) illustrates two flow channels used in a pump impeller according to an embodiment of the preset invention, and is a plan view.
  • FIG. 3(A) illustrates a pump impeller provided with the flow channels disclosed in FIGS. 2(A) and 2(B) , and is a perspective view seen from the intake port side.
  • FIG. 3(B) illustrates a pump impeller provided with the flow channels disclosed in FIGS. 2(A) and 2(B) , and is a side view.
  • FIG. 4(A) illustrates the pump impeller disclosed in FIGS. 3(A) and 3(B) , and is a plan view.
  • FIG. 4(B) illustrates the pump impeller disclosed in FIGS. 3(A) and 3(B) , and is a side view.
  • FIG. 4(C) illustrates the pump impeller disclosed in FIGS. 3(A) and 3(B) , and is a bottom view (intake port side).
  • FIG. 5(A) is a sectional view of the pump impeller disclosed in FIGS. 4(A), 4(B) and 4(C) , taken along the line 5 A- 5 A in FIG. 4(A) .
  • FIG. 5(B) is a sectional view of the pump impeller disclosed in FIGS. 4(A), 4(B) and 4(C) , taken along the line 5 B- 5 B in FIG. 4(B) .
  • FIG. 6(A) illustrates three flow channels used in a pump impeller according to a second embodiment of the preset invention, and is a perspective view illustrating the shape of the flow channels.
  • FIG. 6(B) illustrates three flow channels used in a pump impeller according to a second embodiment of the preset invention, and is a plan view.
  • FIG. 7 is a sectional view of the pump impeller disclosed in FIG. 6 .
  • FIG. 8(A) is a sectional view illustrating a pump impeller with flow channels each having a different size and shape, which is a combination of one thin flow channel and two thick flow channels.
  • FIG. 8(B) is a sectional view illustrating a pump impeller with flow channels each having a different size and shape, in which angular intervals are different for each flow channel.
  • FIG. 9 is a sectional view illustrating an example configuration for a submerged pump provided with a pump impeller according to an embodiment of the preset invention.
  • FIG. 10 is a side view illustrating a conventional pump impeller.
  • FIG. 11 is a sectional view illustrating a submerged pump provided with the pump impeller disclosed in FIG. 10 .
  • FIGS. 1 to 8 A pump impeller according to an embodiment of the preset invention will now be described with reference to FIGS. 1 to 8 .
  • the pump impeller of the embodiment includes a plurality of flow channels that bring an intake port coaxial with an axis of rotation into communication with a discharge port on an outer circumferential portion and the flow channels are disposed at an equal angular interval with respect to the axis of rotation by logical add.
  • FIGS. 3(A) to 5(B) illustrate an embodiment with two flow channels
  • FIGS. 6(A) to 8(B) illustrate an embodiment with three flow channels.
  • the flow channels are bent in a curved shape between the intake port and the discharge port.
  • the pump impeller is produced by casting. However, as long as strength or corrosion resistance can be secured, any other metal or non-metal material may be used.
  • FIG. 1(A) is an image by computer graphics, illustrating a flow channel 3 used in a pump impeller.
  • the flow channel is coaxial with the axis of rotation C near the intake port 5 .
  • the central axis of the flow channel 3 near the intake port 5 is parallel to and coincident with the axis of rotation C.
  • the central axis of the flow channel 3 extends downward and then radially outward with respect to the axis of rotation C.
  • a transitional portion from the direction of the axis of rotation to the radially outward direction is formed of a continuous curve.
  • the central axis of the flow channel 3 extends radially outward, it further extends circumferentially with respect to the axis of rotation C. Accordingly, as a result of a combination of the radially outward component with the circumferential component, the central axis of the flow channel 3 extends outward in a spiral manner.
  • the cross-sectional shape of the flow channel 3 is a complete circle near the intake port 5 , while it is rectangular near the discharge port 7 . Accordingly, a transitional region from the intake port 5 toward the discharge port 7 continuously changes such that a circle gradually turns into a rectangle. Note that even though the term rectangle is used, corner portions do not have right-angled surfaces but are formed of curves of a small radius of curvature. This arrangement is for preventing foreign matters from being accumulated in the corner portions.
  • FIG. 1(A) illustrates a logical shape of the flow channel 3 ; when applied to an actual pump impeller, an outer edge of the pump impeller is circular about the axis of rotation C. Specifically, an ellipse illustrated in FIG. 1(A) defines the outer edge of the pump impeller. Accordingly, an actual flow channel 3 formed in the pump impeller has a shape as illustrated in FIG. 1(B) in which the discharge port 7 is formed over a broad angular range.
  • the shape of the flow channel 3 used in a pump impeller has been described. This description, however, is of a case in which only one flow channel 3 is provided. As described below, the embodiment is characterized by a combination of two flow channels, and thus a specific example thereof will be described.
  • FIG. 2(A) illustrates a configuration that includes two flow channels 13 A and 13 B and that has been subjected to logical add with reference to the axis of rotation C (intake port).
  • the flow channels 13 A and 13 B have completely the same size and shape as each other and are located at point-symmetric positions with respect to the central axis C.
  • the flow channel 3 in FIGS. 1(A) and 1(B) is rotationally copied and disposed at an equal angular interval.
  • regions where the flow channels 13 A and 13 B are directed radially outward from an intake port 15 extend in directions mutually spaced by 180° (opposite directions).
  • the logical add used herein refers to simply combining two flow channels with a common intake port.
  • FIG. 2(B) illustrates actual flow channels 13 A and 13 B by the outer edge of the pump impeller (illustrated by a dotted line), similarly to FIG. 1(B) .
  • the flow channels 13 A and 13 B are completely point-symmetric with respect to the axis of rotation C, and form a generally S-shaped flow channel as a whole.
  • discharge ports 17 A and 17 B are formed over a broad angular range, similarly to the example in FIG. 1(B) .
  • FIGS. 3 are views of a pump impeller 11 according to the embodiment created by computer graphics.
  • FIG. 3(A) is a view seen obliquely from the intake port 15 side
  • FIG. 3(B) is a view seen from the side.
  • Flow channels formed inside the pump impeller 11 illustrated in the figure are the flow channels 13 A and 13 B illustrated in FIG. 2(B) .
  • the cross-sectional shape of a flow channel is nearly circular on the right side (upstream side) of the axis of rotation C, while it is in a shape forming a part of a rectangle on the left side (downstream side) of the axis of rotation.
  • FIGS. 4(A), 4(B) and 4(C) illustrate the pump impeller 11 of the embodiment, and are a plan view, a side view, and a bottom view, respectively.
  • a cylindrical hub 14 is formed in a region of the central axis C, and the hub 14 is adapted to receive an inserted driving shaft (not illustrated) of a driving motor.
  • the pump impeller 11 is adapted to rotate at the number of revolution on the order of 1500 rpm. However, if efficiency can be improved, the pump impeller may be rotated at any number of revolution that is lower or higher than 1500 rpm.
  • FIG. 5(A) is a sectional view taken along the line 5 A- 5 A in FIG. 4(B) .
  • the pump impeller 11 includes an intake port 15 formed therein that is open to one side of the central axis C, and sewage is taken in as the pump impeller 11 rotates. The sewage is then transported from the intake port 15 circumferentially outward along the flow channels 13 A and 13 B, finally drained from the discharge ports 17 A and 17 B.
  • a driving shaft is inserted in the opening as described above, and thus the sewage will not leak from the opening.
  • FIG. 5(B) is a sectional view taken along the line 5 B- 5 B in FIG. 4(B) .
  • the flow channels 13 A and 13 B continuing from the intake port 15 extend radially outward in a spiral manner, and provide discharge ports 17 A and 17 B on the outer edge of the pump impeller 11 .
  • other portions than the flow channels are wall portions constituting the pump impeller 11 .
  • the discharge ports 17 A and 17 B of the embodiment are formed in an angular range of approximately 180° with respect to the central axis C. This is based on a basic idea that there are two flow channels 13 A and 13 B and that efficiency is improved by forming discharge ports 17 A and 17 B over as broad angular range as possible.
  • a pump casing 16 is also illustrated for convenience in explanation. Description will be made later as to how the pump impeller 11 and the pump casing 16 are related.
  • the intake port 15 is cylindrical and is open so as to be coaxial with the axis of rotation C. Accordingly, the intake port 15 is formed as substantially common one port by logical add.
  • the intake port 15 is disposed so as to be open downward when it is actually installed in a pump.
  • the inner diameter of the intake port 15 is set based on the volume of solid matters contained in sewage handled by the pump impeller 11 .
  • the flow channels 13 A and 13 B branch out from one intake port 15 into two flow channels, as described above.
  • the flow channels 13 A and 13 B have approximately the same cross-sectional area from near the intake port 15 up to the junction.
  • the cross-sectional area is gradually reduced from the junction toward the downstream. This is because if the cross-sectional area of each of the flow channels 13 A and 13 B is equivalent to the cross-sectional area of the intake port 15 after branching, the sum of the areas doubles and the pressure of sewage decreases, which may cause a separation phenomenon of sewage from an inner surface of the flow channels 13 A and 13 B.
  • the rate of decrease in the cross-sectional area of the flow channels 13 A and 13 B after branching varies depending on the nature of sewage handled or parameters such as the number of revolution of the pump impeller 11 .
  • the separation phenomenon is less likely to occur so that the rate of decrease in the cross-sectional area may be small.
  • the separation phenomenon is likely to occur so that the rate of decrease in the cross-sectional area may desirably be increased.
  • the cross-sectional area of the flow channels 13 A and 13 B after branching is approximately 0.55 (in the case of two flow channels) per unit of the cross-sectional area of the intake port 15 .
  • the inner wall surfaces of the flow channels 13 A and 13 B near the junction is formed to have a surface roughness different from each other. This is to address the case in which fibrous objects (elongated string-like objects) are preset in sewage. For example, assume that a fibrous object on the order of several tens of centimeters long is preset in sewage. In this case, opposite ends of the fibrous object may possibly flow in two flow channels 13 A and 13 B separately. If such a case happens, the fibrous object sticks to and remains in the junction.
  • fibrous objects elongated string-like objects
  • the fibrous object is allowed to flow in one of the flow channels 13 A and 13 B smoothly.
  • the inner surface of one flow channel 13 A is smoothened, and the inner surface of the other flow channel 13 B is formed in a roughened state (for example, as-cast state).
  • the frictional resistance on the fibrous object is lower on the smooth inner surface, and to the contrary, the coefficient of friction is higher on the rough inner surface.
  • Such imbalance in the coefficient of friction allows the fibrous object to flow in the side of the flow channel having the smooth inner surface. In this way, a possible problem that may be associated with two flow channels 13 A and 13 B can be solved by intentionally altering the surface roughness.
  • the pump impeller 11 rotates clockwise in FIG. 5(B) .
  • sewage preset in the (first) flow channel 13 A of the pump impeller 11 is subjected to a centrifugal force associated with the rotation. For this reason, the sewage tends to move outward in the radial direction of the pump impeller 11 .
  • the discharge port 17 A of the pump impeller 11 faces a drain port 18 of the pump casing 16 , the sewage is then delivered to the outside of the pump through the discharge port 17 A and the drain port 18 .
  • the flow channels 13 A and 13 B are subjected to a pressure drop.
  • sewage is taken in from the intake port 15 .
  • the cross-sectional area of the flow channels 13 A and 13 B is defined to prevent sewage from separating from the inner surface of the flow channels 13 A and 13 B near the discharge ports 17 A and 17 B, as described above.
  • the cross-sectional area of the flow channels 13 A and 13 B may be gradually changed from the intake port 15 toward the discharge ports 17 A and 17 B, or may be constant in a predetermined section and constant at a different scale in other sections.
  • the flow channels 13 A and 13 B of the embodiment have a cross-sectional shape that changes from circular to rectangular between the intake port 15 and the discharge ports 17 A and 17 B.
  • these cross-sectional shapes are only exemplary. Sequentially from the intake port 15 to discharge ports 17 A and 17 B, any combination may be made, for example: circular -> a transitional region -> elliptic, or circular -> a transitional region -> elliptic -> a transitional region -> rectangular.
  • rectangular in the embodiment refers to a square, an oblong cross-sectional shape may be used.
  • All inner wall surfaces of the flow channels 13 A and 13 B are formed of a continuous curved surface. This is to prevent the flow channels 13 A and 13 B from being clogged with foreign matters.
  • the cross-sectional shape of the flow channels 13 A and 13 B is rectangular near the discharge ports 17 A and 17 B. Corner portions of the cross-section are not completely right-angled but are connected by a continuous curved surface. Furthermore, a longitudinal axis (a line connecting sectional centers from the intake port 15 to the discharge ports 17 A and 17 B) of the flow channels 13 A and 13 B is also continuous. In this way, foreign matters are prevented from being caught in the flow channels 13 A and 13 B while sewage is flowing.
  • FIGS. 6(A), 6(B) and 7 are views for describing a pump impeller 21 with three flow channels according to a second embodiment.
  • FIG. 6(A) corresponds to FIG. 2(A) of the first embodiment
  • FIG. 6(B) corresponds to FIG. 2(B)
  • FIG. 7 corresponds to FIG. 5 .
  • FIGS. 6(A) and 6(B) illustrate three flow channels 23 A, 23 B and 23 C disposed in positions located at an equal angular interval around an intake port 25 .
  • the flow channels 23 A, 23 B and 23 C have completely the same size and shape as each other and formed by rotationally copying the flow channel in FIGS. 1(A) and 1(B) and disposing them at an equal angular interval with respect to the central axis C. Accordingly, as illustrated in FIG. 6(B) , regions where the flow channels 23 A, 23 B and 23 C are directed radially outward from the intake port 25 extend in directions mutually spaced by 120°.
  • FIG. 6(B) illustrates actual flow channels 23 A, 23 B and 23 C by an outer edge of the pump impeller 23 (illustrated by a dotted line), similarly to FIG. 2(B) .
  • discharge ports 27 A, 27 B and 27 C are formed over a broad angular range (approximately) 120°, similarly to the example in FIG. 2(B) .
  • FIG. 7 is a sectional view illustrating a pump impeller housed in an actual pump casing 26 .
  • sewage is drained by one third per rotation from three flow channels 23 A, 23 B and 23 C, respectively.
  • the drain flow rate is the same, pressure variation occurring during drainage is kept lower than that of the pump impeller 11 of the first embodiment with two flow channels.
  • a pump impeller capable of reducing fluid balance is not necessarily limited to the pump impeller of the above configuration.
  • the fluid balance can be reduced when one flow channel is thinner and the remaining two flow channels are thicker, as illustrated in FIG. 8(A) .
  • a combination of two thinner flow channels and one thicker flow channel is also possible.
  • the fluid balance can be reduced when angular intervals between flow channels are unequal.
  • an intermittent flow (pulsation) in a volute can be increased to enhance drainability for foreign matters.
  • FIG. 9 is a sectional view of a submerged pump 60 provided with the pump impeller 11 according to the embodiment as described above.
  • the pump impeller 11 is contained in a pump casing 62 and connected to a closed-type submerged motor 63 for rotatably driving the pump impeller 11 .
  • the submerged motor 63 includes a motor 66 having a stator 64 and a rotor 65 , and a motor casing 67 that covers the motor 66 .
  • a driving shaft 68 extending vertically is provided at the center portion of the rotor 65 .
  • the driving shaft 68 is rotatably supported by bearings 69 and 70 at the upper end portion and an intermediate portion on the lower side, respectively.
  • the pump impeller 11 is then connected to the lower end portion of the driving shaft 68 .
  • a pump chamber 76 which is partitioned by an inner wall 75 that is recessed in a semicircular shape in its cross section, is formed within the pump casing 62 .
  • a discharge portion 68 of the pump impeller 11 is contained in the pump chamber 76 .
  • An intake portion 71 that protrudes downward is formed in the lower portion of the pump casing 62 .
  • An intake port 72 that is open downward is formed in the intake portion 71 .
  • a drain portion 73 that protrudes laterally is formed on the side portion of the pump casing 62 .
  • the drain portion 73 includes a drain port 74 formed therein, which is open laterally.
  • a pump impeller according to the preset invention can be particularly useful for a submerged pump for sewage.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
US14/439,879 2013-07-05 2014-04-15 Pump impeller for submerged pump and submerged pump including same Abandoned US20160108927A1 (en)

Applications Claiming Priority (3)

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
PCT/JP2014/060657 WO2015001830A1 (fr) 2013-07-05 2014-04-15 Ailette de pompe pour pompe immergée et pompe immergée comprenant celle-ci

Publications (1)

Publication Number Publication Date
US20160108927A1 true US20160108927A1 (en) 2016-04-21

Family

ID=52143424

Family Applications (1)

Application Number Title Priority Date Filing Date
US14/439,879 Abandoned US20160108927A1 (en) 2013-07-05 2014-04-15 Pump impeller for submerged pump and submerged pump including same

Country Status (7)

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

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
KR101816766B1 (ko) 2016-09-02 2018-01-09 이신구 에너지 절감형 펌프
RU2735971C1 (ru) * 2020-02-25 2020-11-11 Игорь Олегович Стасюк Рабочее колесо ступени лопастного насоса
RU211070U1 (ru) * 2022-01-14 2022-05-19 Константин Георгиевич Мухамадеев Ступень погружного многоступенчатого центробежного насоса
FR3154772A1 (fr) * 2023-10-30 2025-05-02 Faivre Group Rotor monocanal a corps evide

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP6351216B2 (ja) 2013-07-05 2018-07-04 株式会社荏原製作所 水中ポンプ用ポンプ羽根及びこれを備えた水中ポンプ
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
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.
KR102676773B1 (ko) * 2023-07-19 2024-06-19 건우중공업 주식회사 이물질 막힘이 없는 무폐쇄형 임펠러 및 이를 구비하는 수중펌프

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US6405748B1 (en) * 1999-03-22 2002-06-18 David Muhs Trailer and fuel tank assembly
US7677864B2 (en) * 2005-10-12 2010-03-16 K-Tron Technologies, Inc. Bulk material pump feeder with reduced disk jamming, compliant disks
US8535000B2 (en) * 2009-04-24 2013-09-17 Syncrude Canada Ltd. Centrifugal pump for slurries

Family Cites Families (19)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1975274A (en) * 1932-08-17 1934-10-02 Byron Jackson Co Centrifugal pump impeller
JPS52107605A (en) * 1976-03-05 1977-09-09 Hitachi Ltd Sewage pump
JPS5591797A (en) * 1978-12-29 1980-07-11 Ebara Corp Vortex type pump
DE3211230A1 (de) * 1982-03-26 1983-09-29 Paul Pleiger Maschinenfabrik, 5810 Witten Kreiselpumpe, insbesondere fuer schmutz- und abwasser
SE461996B (sv) 1988-09-14 1990-04-23 Flygt Ab Slutet loephjul foer pumpar, kompressorer, flaektar etc av centrifugal- eller halvaxiell typ
JPH09209963A (ja) * 1996-02-03 1997-08-12 Nakase Noriyuki 固形物移送用のポンプ
JP2000297789A (ja) 1999-04-14 2000-10-24 Tokyo Electric Power Co Inc:The 軸流圧縮機
FI110275B (fi) 2001-04-27 2002-12-31 Grundfos Management As Pumpun juoksupyörä
US6837684B2 (en) 2002-10-25 2005-01-04 Grundfos Management A/S Pump impeller
JP4713066B2 (ja) 2003-07-18 2011-06-29 新明和工業株式会社 羽根車及びそれを備えた汚水処理用ポンプ
SE0402840L (sv) * 2004-11-19 2006-04-11 Itt Mfg Enterprises Inc Pumphjul
EP1795758A1 (fr) 2005-12-09 2007-06-13 Grundfos Management A/S Roue pour une unité de pompage et unité de pompage
MX2007002934A (es) 2007-03-12 2008-09-17 Calidad Empresarial Dinamica Sa De Cv Bomba centrífuga de alta eficiencia y metodo para el diseño de su impulsor.
CN201377436Y (zh) * 2009-03-31 2010-01-06 长沙水泵厂有限公司 一种双吸多级卧式水平中开泵结构
PL216284B1 (pl) 2010-03-22 2014-03-31 Fundacja Rozwoju Kardiochirurgii Im Prof Zbigniewa Religi Pompa odśrodkowa jednostrumieniowa
TWI464322B (zh) * 2010-12-14 2014-12-11 Delta Electronics Inc 離心式風扇
KR101070136B1 (ko) * 2011-02-22 2011-10-05 이재웅 원통형 베인을 포함하는 임펠러
JP2013141415A (ja) 2012-01-06 2013-07-22 Ihi Corp 単糖の製造方法及び製造装置並びにエタノールの製造方法及び製造装置
JP6351216B2 (ja) 2013-07-05 2018-07-04 株式会社荏原製作所 水中ポンプ用ポンプ羽根及びこれを備えた水中ポンプ

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US6405748B1 (en) * 1999-03-22 2002-06-18 David Muhs Trailer and fuel tank assembly
US7677864B2 (en) * 2005-10-12 2010-03-16 K-Tron Technologies, Inc. Bulk material pump feeder with reduced disk jamming, compliant disks
US8535000B2 (en) * 2009-04-24 2013-09-17 Syncrude Canada Ltd. Centrifugal pump for slurries

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
KR101816766B1 (ko) 2016-09-02 2018-01-09 이신구 에너지 절감형 펌프
RU2735971C1 (ru) * 2020-02-25 2020-11-11 Игорь Олегович Стасюк Рабочее колесо ступени лопастного насоса
RU211070U1 (ru) * 2022-01-14 2022-05-19 Константин Георгиевич Мухамадеев Ступень погружного многоступенчатого центробежного насоса
FR3154772A1 (fr) * 2023-10-30 2025-05-02 Faivre Group Rotor monocanal a corps evide
WO2025093831A1 (fr) 2023-10-30 2025-05-08 Faivre Group Rotor monocanal a corps evide

Also Published As

Publication number Publication date
BR112015009797B1 (pt) 2022-03-15
JP2015014251A (ja) 2015-01-22
EP2930367A4 (fr) 2016-11-02
EP2930367B1 (fr) 2020-05-27
CN104662302A (zh) 2015-05-27
BR112015009797A8 (pt) 2017-08-01
DK2930367T3 (da) 2020-06-29
JP6351216B2 (ja) 2018-07-04
BR112015009797A2 (pt) 2017-07-11
WO2015001830A1 (fr) 2015-01-08
EP2930367A1 (fr) 2015-10-14
CN104662302B (zh) 2017-11-28

Similar Documents

Publication Publication Date Title
EP2930367B1 (fr) Ailette de pompe pour pompe immergée et pompe immergée comprenant celle-ci
RU2659843C2 (ru) Ротор для центробежной проточной машины и центробежная проточная машина
CN101842598A (zh) 侧通道压缩机
CN104487714A (zh) 叶轮以及具备该叶轮的旋转机械
JPWO2013128539A1 (ja) 回転機械
KR20150070294A (ko) 고효율 및 낮은 비속도의 원심 펌프
JPWO2016121046A1 (ja) 遠心圧縮機のケーシング、及び、遠心圧縮機
US10947988B2 (en) Impeller and centrifugal compressor
JP5275264B2 (ja) 排水ポンプ
JP5044105B2 (ja) 遠心ポンプ用羽根車及びそれを備えた遠心ポンプ
JP6908472B2 (ja) 遠心圧縮機
JP4842676B2 (ja) 遠心ポンプ用羽根車および遠心ポンプ用羽根車のバランス調整方法
EP3863759A1 (fr) Réacteur à cavitation
JP2006291917A (ja) 遠心ポンプ用羽根車及びそれを備えた遠心ポンプ
US10082154B2 (en) Intake channel arrangement for a volute casing of a centrifugal pump, a flange member, a volute casing for a centrifugal pump and a centrifugal pump
US10859092B2 (en) Impeller and rotating machine
JP2011236915A (ja) 遠心ポンプ用羽根車及びそれを備えた遠心ポンプ
JP2006132432A (ja) 液体ポンプ
JP4731122B2 (ja) 液体ポンプ
US10107288B2 (en) Housing for scroll compressor and scroll compressor
JP7495202B2 (ja) 遠心ポンプ
KR101784561B1 (ko) 단일 유로 펌프 벌류트 및 이를 구비한 원심 펌프
JP7330508B2 (ja) 羽根車及び水中ポンプ
CN205823725U (zh) 潜水泵用泵叶片以及具备该潜水泵用泵叶片的潜水泵
TW201627578A (zh) 用於水中幫浦的幫浦扇葉以及具備該幫浦扇葉的水中幫浦

Legal Events

Date Code Title Description
AS Assignment

Owner name: EBARA CORPORATION, JAPAN

Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNORS:KAWAI, MASAHITO;SAKACHO, HIROMI;OBUCHI, MASASHI;AND OTHERS;REEL/FRAME:035807/0216

Effective date: 20150304

STPP Information on status: patent application and granting procedure in general

Free format text: ADVISORY ACTION MAILED

STCB Information on status: application discontinuation

Free format text: ABANDONED -- FAILURE TO RESPOND TO AN OFFICE ACTION