CN102099584A - Centrifugal pump impeller and centrifugal pump - Google Patents
Centrifugal pump impeller and centrifugal pump Download PDFInfo
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- CN102099584A CN102099584A CN2009801278878A CN200980127887A CN102099584A CN 102099584 A CN102099584 A CN 102099584A CN 2009801278878 A CN2009801278878 A CN 2009801278878A CN 200980127887 A CN200980127887 A CN 200980127887A CN 102099584 A CN102099584 A CN 102099584A
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- impeller
- centrifugal
- pump
- impeller bodies
- centrifugal blade
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- 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
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Structures Of Non-Positive Displacement Pumps (AREA)
Abstract
A centrifugal pump impeller (11) is provided with an impeller body having an inner flow path (35) formed therein, and also with a single centrifugal impeller (37) mounted to the impeller body such that the position of an exit (34) is the front edge of the centrifugal impeller and a specific position of the outer peripheral edge of the impeller body is the rear edge of the centrifugal impeller. The centrifugal blade (37) is designed such that the ratio between the area of an outer flow path (36) defined by the centrifugal impeller (37), the area having the angular range of 270 degrees in the circumferential direction from the rear edge of the centrifugal impeller (37), and the area of the entire impeller body surrounded by the outer peripheral edge of the impeller body is less than 0.3.
Description
Technical field
Technology disclosed herein relates to a kind of be suitable for transporting for example centrifugal impeller of pump and a kind of centrifugal pump that comprises this centrifugal impeller of pump of sewage etc.
Background technique
Up to now, when transporting sewage etc., use centrifugal pump.In centrifugal pump, comprise impeller and housing as the main composition factor.In impeller, the no obstruction type impeller that is formed with the helical stream in inside has been (for example, with reference to patent documentation 1) known to everybody as the impeller that the sewage that contains solid matter such as slag inclusion etc. is difficult to stop up.
The impeller of patent documentation 1 disclosed centrifugal pump has internal flow path and outside stream, this internal flow path extends upward from the inlet that is formed on the impeller lower surface, this outer flow route centrifugal blade marks off, and makes this outer flow curb outer circumferential face circle round, and is connected with internal flow path.In this centrifugal pump, the percentage by particle diameter (maximum particle diameter of ball that can be by stream) and pumping hole footpath is set at 100%.
Patent documentation 1: a day disclosure special permission communique spy opens the 2005-36778 communique
Summary of the invention
The technical problem that-invention will solve-
Under many circumstances, require this sewage to possess the higher pump characteristics of lift in small flow zone with pump.For satisfying this requirement to pump characteristics, making impeller outer diameter is more greatly a kind of effective method.Yet if make impeller outer diameter bigger, it is bigger to cause the required power of pump.So, the present application persons gaze at following measure, that is: be not only to make impeller outer diameter bigger, but the various factors of change impeller, make the slope of head curve (curve that shows the relation between spray volume and the total head) steeper, thereby make impeller outer diameter bigger in the mode that does not change required power.
For taking described measure, the present application person have expected making the narrower scheme of exit width of impeller.In such event, the ejection flow just diminishes, thereby can realize making the slope of head curve steeper.
Yet the present application person find, if make the exit width of impeller narrower, just diminish by particle diameter, following problems consequently occurs, that is: can not keep by particle diameter is specified value, are 100% etc. with the percentage in pumping hole footpath for example.
Technology disclosed herein is very effective aspect following, that is: in the centrifugal pump of the impeller that comprises the outside stream with helical internal flow path and left and right sides lift, be to make the lift in small flow zone higher under the state of specified value keeping by particle diameter.
-in order to the technological scheme of technical solution problem-
The present application persons have expected making the less scheme of the shared ratio of outside stream on the horizontal section of impeller.This is equivalent to be present in this outside stream and the amount of the fluid that sprays from impeller is fewer.Therefore, under the condition that external diameter equates, the ejection flow of comparing above-mentioned impeller with the relatively large impeller of the shared ratio of outside stream still less.On the other hand, because the exit width (being equivalent to the height on the running shaft direction) of above-mentioned impeller is narrowed down, be specified value so can keep by particle diameter.
A kind of exemplary centrifugal impeller of pump, comprise impeller bodies and a centrifugal blade, in this impeller bodies, be formed with internal flow path, this internal flow path is shape in the shape of a spiral, circling round around running shaft and to extend and make at the inlet of an end face upper shed of this impeller bodies and in the outlet of the side face upper shed of this impeller bodies and couple together along this running shaft direction, this centrifugal blade is arranged in the described impeller bodies, make the position of described outlet become the trailing edge that assigned position on the outer periphery of the leading edge of this centrifugal blade and described impeller bodies becomes this centrifugal blade, and the particle diameter that passes through of described centrifugal impeller of pump is set at specified value.
Described centrifugal blade forms along the angular range that the circumferencial direction that with described running shaft is the center extends more than 270 °.The outside stream that is marked off from the side face of described impeller bodies depression by this centrifugal blade is connected with described outlet, and circle round along the side face of described impeller bodies, described centrifugal blade is designed to: on the horizontal section of the axial central height and position of rotation of described outside stream, the ratio of the area of the described outside stream in 270 ° the angular range of counting from the trailing edge of described centrifugal blade and the entire area of the described impeller bodies of surrounding in a circumferential direction by the outer periphery of described impeller bodies, promptly
Area ratio=(area of outside stream)/(entire area of impeller bodies)
Less than 0.3.
The effect of-invention-
Impeller with described structure can be implemented in and keep by particle diameter is under the state of specified value the lift in small flow zone to be increased.
Description of drawings
Fig. 1 is the longitudinal sectional view of pump in the water;
Fig. 2 is the stereogram of impeller;
Fig. 3 is the transverse sectional view (along the sectional view of the III-III line of Fig. 5) of impeller;
Fig. 4 is the longitudinal sectional view (along the sectional view of the IV-IV line of Fig. 3) of impeller;
Fig. 5 is the longitudinal sectional view (along the sectional view of the V-V line of Fig. 3) of impeller;
Fig. 6 is a pump performance plotted curve (flow coefficient-head coefficient) in the related water of embodiment;
Fig. 7 is a pump performance plotted curve (flow coefficient-power factor) in the related water of embodiment;
Fig. 8 is a pump performance plotted curve (flow coefficient-pump efficiency) in the related water of embodiment.
Description of reference numerals
10 centrifugal pumps
11 impellers (impeller bodies)
12 housings
Motor in 13 water (motor part)
18 live axles (running shaft)
34 outlets
35 internal flow paths
36 outside streams
37 centrifugal blades
Embodiment
A kind of exemplary centrifugal impeller of pump, comprise impeller bodies and a centrifugal blade, in this impeller bodies, be formed with internal flow path, this internal flow path is shape in the shape of a spiral, circling round around running shaft and to extend and make at the inlet of an end face upper shed of this impeller bodies and in the outlet of the side face upper shed of this impeller bodies and couple together along this running shaft direction, this centrifugal blade is arranged in the described impeller bodies, make the position of described outlet become the trailing edge that assigned position on the outer periphery of the leading edge of this centrifugal blade and described impeller bodies becomes this centrifugal blade, and the particle diameter that passes through of described centrifugal impeller of pump is set at specified value.
Described centrifugal blade forms along the angular range that the circumferencial direction that with described running shaft is the center extends more than 270 °.The outside stream that is marked off from the side face of described impeller bodies depression by this centrifugal blade is connected with described outlet, and circle round along the side face of described impeller bodies, described centrifugal blade is designed to: on the horizontal section of the axial central height and position of rotation of described outside stream, the area of the described outside stream in 270 ° the angular range of counting from the trailing edge of described centrifugal blade and the ratio of the entire area of the described impeller bodies of being surrounded by the outer periphery of described impeller bodies are less than 0.3 in a circumferential direction.
According to described structure, centrifugal blade is designed to: on the horizontal section of regulation, the entire area of the area of the described outside stream in 270 ° the angular range of counting from the trailing edge of centrifugal blade and the impeller bodies of being surrounded by the outer periphery of impeller bodies (promptly in a circumferential direction, the area of the circle that surrounds by outer periphery) ratio, promptly in value that this area with outside stream obtains divided by the entire area of impeller bodies (below, also abbreviate as area than) less than 0.3.Remark additionally, described area ratio is greater than 0.That is to say that in this impeller, outside stream shared ratio on the horizontal section of this impeller is less.This is equivalent to be present in the outside stream and the amount of the fluid that sprays from impeller is fewer.Therefore, equate with external diameter and ejection flow that described area is compared above-mentioned impeller than relatively large impeller still less.Thus, comprise that the slope of head curve of centrifugal pump of the impeller with this structure is steeper, and air horsepower is lower.Consequently, can use compared with prior art required power about equally but the bigger impeller bodies of external diameter, lift increases.That is to say, can realize making the lift in small flow zone to increase.
Also have, according to described structure, the lateral cross-sectional area that is set at outside stream is less, and does not make the outlet narrowed width.Thus, can keep by particle diameter is specified value.Therefore, according to impeller, can be implemented in that to keep by particle diameter be under the state of specified value the lift in small flow zone to be increased with described structure.The described percentage that can be set at pumping hole footpath by particle diameter is 100%.
A kind of exemplary centrifugal pump comprises: described centrifugal impeller of pump, take in the housing of described centrifugal impeller of pump and drive the motor of described centrifugal impeller of pump rotation.As mentioned above, according to this centrifugal pump, can realize making the lift in small flow zone to increase.
Below, the mode of execution to impeller is illustrated with reference to the accompanying drawings.Remark additionally example only on the illustrative in nature of following preferred implementation.As shown in Figure 1, example pump is a pump in the sewage treatment water.Pump is made of centrifugal pump 10 in this water, comprises impeller 11, covers the housing 12 of impeller 11 and makes motor 13 in the enclosed type water of impeller 11 rotations.
Motor 13 comprises motor 16 that is made of stator 14 and rotor 15 and the motor casing 17 that covers motor 16 in the water.Core at rotor 15 is provided with the live axle 18 that extends along the vertical direction.This live axle 18 is supported for rotation freely by upper bearing 19 and lower bearing 20.The underpart of live axle 18 and impeller 11 connect, the rotary driving force of live axle 18 motor 13 in impeller 11 transmission water.
Housing 12 has the volute chamber 26 that covers impeller 11 in the inside of this housing 12.Volute chamber 26 is divided and is formed by the ground of semicircular in shape on longitudinal sectional view curved sidewall 12a.The width (height on the running shaft direction) of in the axial direction width of this volute chamber 26 (width on the above-below direction among Fig. 1, in other words, the height on the running shaft direction) and the outlet 34 of impeller 11 described later about equally.
Form outstanding suction portion 21 downwards in the lower end of housing 12.In this suction portion 21, be formed with the suction port 22 of opening downwards.Suction port 22 is communicated with the inlet 33 of impeller 11 described later.On the other hand, the sidepiece at housing 12 forms the outstanding ejection portion 23 of oriented side.This ejection portion 23 is communicated with volute chamber 26, is formed with the ejiction opening 24 to side openings in ejection portion 23.In the present embodiment, the closer to the downstream side of ejection portion 23, the stream diameter of ejection portion 23 is just big more, but is not limited to this, also can set the stream diameter and be certain constant value.The diameter of the diameter of the inlet of ejection portion 23 (connection mouth that is connected with volute chamber 26) and the outlet 34 of impeller described later 11 about equally.That is to say that ejection portion 23 is set at by the pass through particle diameter of particle diameter with the internal flow path 35 of impeller 11 and equates, this pump to pass through the percentage that particle diameter is set at pumping hole footpath be 100%.In this pump, the lowest calibre of ejection portion 23 is equivalent to the pumping hole footpath.Remark additionally, as long as ejection portion 23 passes through particle diameter passing through more than the particle diameter at internal flow path 35.
As Fig. 2～shown in Figure 5, impeller 11 has the approximate cylinder shape that comprises upper-end surface and lower end surface and the side face between this two sides.Remark additionally, the crosshatch among Fig. 3 (cross-hatching) is not the expression section, but represents outside stream 36 described later.On the lower end surface of impeller 11, be formed with the inlet 33 of opening downwards, on the other hand, on the side face of impeller 11, be formed with outlet 34 to side openings.Also have, impeller 11 portion within it has the internal flow path 35 that is circling round and extending along this running shaft direction around running shaft, and this internal flow path 35 makes inlet 33 and exports 34 and is connected to each other.Therefore, the position in the axial direction, stream center of internal flow path 35 changes.As shown in Figure 3, the direction opening that extended to internal flow path 35 of outlet 34.The internal flow path 35 that comprises inlet 33 and outlet 34 constitutes: become the value of setting according to the diameter of going back the pipeline of close upstream sides than centrifugal pump 10 by particle diameter.At this, the diameter of internal flow path 35 is set at bigger value, becomes specified value to allow by particle diameter.
Being formed with this outer circumferential face side in diametric on the outer circumferential face of impeller 11 caves in and the outside stream 36 of formation.This outside stream 36 is not the stream that extends along the running shaft direction, but stream that should outside stream 36 is centered close on the vertical surface that the running shaft with impeller 11 intersects vertically.As shown in Figure 3, outside stream 36 is connected with the downstream side of internal flow path 35 in outlet 34.The circle round above length of half cycle of impeller 11 of outside stream 36.Particularly, the downstream of outside stream 36 extend to outlet 34 near, outside thus stream 36 extends 270 ° angular range along the circumferencial direction that with the running shaft is the center.Remark additionally, more than 270 ° and the length of suitably setting outside stream 36 in less than 360 ° scope get final product.
This outside stream 36 is marked off by blade 37.This blade 37 is so-called radial-flow type (radialflow) blades (centrifugal blade).Water in 37 pairs of outside streams 36 of this centrifugal blade boosts, and sprays this water to outer circumferential side (radial outside).At this, centrifugal blade 37 not only marks off outside stream 36, also marks off internal flow path 35 with its inboard face.Centrifugal blade 37 forms along the angular range that the circumferencial direction that with the running shaft is the center extends more than 270 °.In the present embodiment, the angular range that specially is set at 270 ° of these centrifugal blade 37 extensions forms, and outside thus stream 36 extends 270 ° angular range, as mentioned above.Also have, in the present embodiment, the exit angle of centrifugal blade 37 is set at smaller value.Particularly, exit angle is about 10 °.
Also have, the leading edge locus of centrifugal blade 37 is set in the position in the comparison outside radially, make the lateral cross-sectional area of described outside stream 36 smaller thus.That is to say, centrifugal blade 37 is set at: externally on the horizontal section of the axial central height and position of rotation of stream 36, the area ratio of the lateral cross-sectional area (having drawn the area in cross-hatched zone among Fig. 3) of outside stream 36 and the impeller entire area (area of the circle among Fig. 3) of being surrounded by the outer periphery of impeller 11 is about to the value that the area of outside stream 36 obtains divided by the entire area of impeller (area than) less than 0.3.As mentioned above, in this impeller 11, the lateral cross-sectional area of setting outside stream 36 is smaller value, thereby it is less to be present in the amount of the fluid in this outside stream 36.Thus, the ejection flow of this impeller 11 is less, and the slope of head curve is steeper, and air horsepower is lower, and is as described below.Remarking additionally, also can be such, that is: be used for dividing and constituting the design function of outside stream 36 by suitably changing, thereby make the change in shape of this outside stream 36, makes described area than less than 0.3, replaces changing the position of leading edge.
At this, in this impeller 11, be used for dividing and constitute the design function of internal flow path 35 and be used for dividing and to constitute the design function of outside stream 36 different, thereby under design usually, internal flow path 35 is connected near the outlet 34 of internal flow path 35 with outside stream 36 unsmoothly.Yet, in the present embodiment, because near near (among Fig. 3 the position of symbol 100 indications) chamfering end of centrifugal blade 37, so internal flow path 35 is connected smoothly with outside stream 36.Therefore, the leading edge of the centrifugal blade 37 of this impeller 11 is more not obvious.Remark additionally, in impeller shown in Figure 3 11, the position that the outer side surface of the dot and dash line that extends longitudinally among Fig. 3 and centrifugal blade 37 intersects just is equivalent to the leading edge of centrifugal blade 37.
In impeller 11,, be formed with on whole week all to the first outstanding lip part 38 of side than the position of outside stream 36 also close upsides.Also have,, be formed with same second lip part of on whole week, all giving prominence to 39 to side at position than outside stream 36 also close downsides.Second lip part 39 will separate up and down in the impeller 11 and constitutes the upper portion that is formed with inlet 33 lower portion and is formed with outlet 34.That is to say that this impeller 11 is the double shrouded wheels that separated by second lip part 39 between inlet 33 and the outlet 34.At this, shown in Fig. 4 waited, first lip part 38 of this impeller 11 was set at the width (height on the running shaft direction) of described outlet 34 with interval between second lip part 39 and equates.
Remark additionally, the core in the upper-end surface of impeller 11 is provided with hub portion 31, is formed with the mounting hole 32 that is used for allowing the top of live axle 18 insert in this hub portion 31.
Described centrifugal pump 10 ejection sewage as described below.That is to say that motor 13 makes impeller 11 rotation in the water, impeller 11 is drawn sewage upward from the inlet 33 of the downside that is positioned at this impeller 11.The sewage that has been inhaled into is by the internal flow path 35 in the impeller 11, flows through outlet 34 and arrives outside stream 36.Centrifugal blade 37 has arrived the sewage of outside stream 36 to the outer circumferential side ejection.The housing 12 that covers impeller 11 receives the sewage that has been ejected.Sewage flow through after in flowing through volute chamber 26 ejiction opening 24 by row to the pump outside.
Then, the embodiment to concrete enforcement is illustrated.Fig. 6～Fig. 8 shows the performance curve of the centrifugal pump 10 that comprises each impeller 11 that makes the variation of described area ratio respectively.Fig. 6 shows the head coefficient with respect to flow coefficient; Fig. 7 shows the power factor with respect to flow coefficient; Fig. 8 shows the pump efficiency with respect to flow coefficient.Remark additionally, the note on the use among Fig. 6～Fig. 8 is common, only figure 6 illustrates the note on the use.At this, each impeller 11 is set at: its external diameter, the width of outlet 34, the posterior border position and the exit angle (10 °) of centrifugal blade 37 are equal to each other, and the leading edge locus of centrifugal blade 37 is different, make the transverse cross-sectional shape of centrifugal blade 37 different thus, thereby make the lateral cross-sectional area of outside stream 36, and then make described area more unequal than mutually.That is to say, be positioned at radial outside by the leading edge locus that makes centrifugal blade 37, it is less relatively that the lateral cross-sectional area of then outside stream 36 becomes, the area ratio reduces, on the other hand, be positioned at radially inner side by the leading edge locus that makes centrifugal blade 37, the lateral cross-sectional area of then outside stream 36 becomes relatively large, and area is than increasing.Remark additionally, 0.252 and 0.230 area is than being equivalent to embodiment respectively.0.375 the area ratio be equivalent to conventional example, 0.203 area ratio is equivalent to comparative example.
By the result of Fig. 6～Fig. 8 as seen, by with area than reducing gradually and become 0.252,0.230 and 0.203 successively since 0.375, the slope of head curve steepening gradually then, power factor descends gradually.But if allow the area ratio become too small, the zero delivery lift just can descend, pump efficiency can descend on the whole (reference point X).Therefore, by present embodiment as seen,, just preferably set area than for less than the value more than 0.30 and 0.23 if will make the slope of head curve steep and make power factor lower.
Therefore, at the impeller 11 and the centrifugal pump 10 of this example,, make the slope of head curve steeper, and air horsepower is descended by setting area than for less than 0.3 value.Therefore, can use compared with prior art required power about equally but the bigger impeller 11 of external diameter, lift increases thereupon.Consequently, this centrifugal pump 10 can realize making the lift in small flow zone to increase.
Also have, the exit angle of setting centrifugal blade 37 is smaller value, and this also helps to allow the slope steepening of head curve.Therefore, impeller 11 and centrifugal pump 10 in this example, set described area than for smaller value with to set exit angle be that smaller value is (in this example, being about 10 °) these two measures combine, the slope of head curve becomes steeper, thereby can realize centrifugal pump 10 is increased at the lift in small flow zone with higher level.
-industrial applicability-
As mentioned above, technology disclosed herein to the centrifugal pump that transports fluid of great use, such as to sewage treatment pump of transporting the sewage that contains field trash etc. etc. of great use.
Claims (4)
1. centrifugal impeller of pump, comprise impeller bodies and a centrifugal blade, in this impeller bodies, be formed with internal flow path, this internal flow path is shape in the shape of a spiral, circling round around running shaft and to extend and make at the inlet of an end face upper shed of this impeller bodies and in the outlet of the side face upper shed of this impeller bodies and couple together along this running shaft direction, this centrifugal blade is arranged in the described impeller bodies, make the position of described outlet become the trailing edge that assigned position on the outer periphery of the leading edge of this centrifugal blade and described impeller bodies becomes this centrifugal blade, and the particle diameter that passes through of described centrifugal impeller of pump is set at specified value, it is characterized in that:
Described centrifugal blade forms along the angular range that the circumferencial direction that with described running shaft is the center extends more than 270 °, the outside stream that is marked off from the side face of described impeller bodies depression by this centrifugal blade is connected with described outlet, and circles round along the side face of described impeller bodies;
Described centrifugal blade is designed to: on the horizontal section of the axial central height and position of rotation of described outside stream, the area of the described outside stream in 270 ° the angular range of counting from the trailing edge of described centrifugal blade and the ratio of the entire area of the described impeller bodies of being surrounded by the outer periphery of described impeller bodies are less than 0.3 in a circumferential direction.
2. centrifugal impeller of pump according to claim 1 is characterized in that:
Described percentage by particle diameter and pumping hole footpath is 100%.
3. centrifugal pump, comprise: centrifugal impeller of pump, take in the housing of described centrifugal impeller of pump and drive the motor that described centrifugal impeller of pump rotates, described centrifugal impeller of pump comprises impeller bodies and a centrifugal blade, in this impeller bodies, be formed with internal flow path, this internal flow path is shape in the shape of a spiral, circling round around running shaft and to extend and make at the inlet of an end face upper shed of this impeller bodies and in the outlet of the side face upper shed of this impeller bodies and couple together along this running shaft direction, this centrifugal blade is arranged in the described impeller bodies, make the position of described outlet become the trailing edge that assigned position on the outer periphery of the leading edge of this centrifugal blade and described impeller bodies becomes this centrifugal blade, and the particle diameter that passes through of described centrifugal impeller of pump is set at specified value, it is characterized in that:
Described centrifugal blade forms along the angular range that the circumferencial direction that with described running shaft is the center extends more than 270 °, the outside stream that is divided out from the side face of described impeller bodies depression by this centrifugal blade is connected with described outlet, and circles round along the side face of described impeller bodies;
Described centrifugal blade is designed to: on the horizontal section of the axial central height and position of rotation of described outside stream, the area of the described outside stream in 270 ° the angular range of counting from the trailing edge of described centrifugal blade and the ratio of the entire area of the described impeller bodies of being surrounded by the outer periphery of described impeller bodies are less than 0.3 in a circumferential direction.
4. centrifugal pump according to claim 3 is characterized in that:
Described percentage by particle diameter and pumping hole footpath is 100%.
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2008187795 | 2008-07-18 | ||
| JP2008-187795 | 2008-07-18 | ||
| PCT/JP2009/003332 WO2010007780A1 (en) | 2008-07-18 | 2009-07-15 | Centrifugal pump impeller and centrifugal pump |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN102099584A true CN102099584A (en) | 2011-06-15 |
Family
ID=41550190
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN2009801278878A Pending CN102099584A (en) | 2008-07-18 | 2009-07-15 | Centrifugal pump impeller and centrifugal pump |
Country Status (5)
| Country | Link |
|---|---|
| US (1) | US20110164968A1 (en) |
| JP (1) | JPWO2010007780A1 (en) |
| CN (1) | CN102099584A (en) |
| CA (1) | CA2731127A1 (en) |
| WO (1) | WO2010007780A1 (en) |
Families Citing this family (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP5384322B2 (en) * | 2009-12-28 | 2014-01-08 | 株式会社荏原製作所 | Pump impeller and submersible pump equipped with the impeller |
| CN102345630B (en) * | 2010-07-26 | 2015-10-21 | 株式会社久保田 | Impeller of pump and pump |
| CN103195755B (en) * | 2013-04-11 | 2015-10-07 | 南京布鲁克林环保设备有限公司 | A kind of single blade screw centrifugal impeller |
Citations (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2005036778A (en) * | 2003-07-18 | 2005-02-10 | Shin Meiwa Ind Co Ltd | Impeller and pump for sewage disposal having the impeller |
| JP2006132432A (en) * | 2004-11-05 | 2006-05-25 | Shin Meiwa Ind Co Ltd | Liquid pump |
| JP2006291917A (en) * | 2005-04-14 | 2006-10-26 | Shin Meiwa Ind Co Ltd | Impeller for centrifugal pump and centrifugal pump having the same |
Family Cites Families (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US2655868A (en) * | 1947-09-08 | 1953-10-20 | Fairbanks Morse & Co | Bladeless pump impeller |
| FI73501C (en) * | 1984-06-06 | 1987-10-09 | Sarlin Ab Oy E | Impeller at a pump. |
| JP4402906B2 (en) * | 2003-06-11 | 2010-01-20 | 株式会社鶴見製作所 | Single blade impeller for submersible pump |
| JP4731122B2 (en) * | 2004-02-27 | 2011-07-20 | 新明和工業株式会社 | Liquid pump |
| JP5118951B2 (en) * | 2007-12-11 | 2013-01-16 | 新明和工業株式会社 | Centrifugal pump impeller and centrifugal pump |
| JP2009221976A (en) * | 2008-03-17 | 2009-10-01 | Shinmaywa Industries Ltd | Impeller for centrifugal pump and centrifugal pump |
-
2009
- 2009-07-15 WO PCT/JP2009/003332 patent/WO2010007780A1/en active Application Filing
- 2009-07-15 CN CN2009801278878A patent/CN102099584A/en active Pending
- 2009-07-15 CA CA2731127A patent/CA2731127A1/en not_active Abandoned
- 2009-07-15 US US13/054,544 patent/US20110164968A1/en not_active Abandoned
- 2009-07-15 JP JP2010520774A patent/JPWO2010007780A1/en active Pending
Patent Citations (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2005036778A (en) * | 2003-07-18 | 2005-02-10 | Shin Meiwa Ind Co Ltd | Impeller and pump for sewage disposal having the impeller |
| JP2006132432A (en) * | 2004-11-05 | 2006-05-25 | Shin Meiwa Ind Co Ltd | Liquid pump |
| JP2006291917A (en) * | 2005-04-14 | 2006-10-26 | Shin Meiwa Ind Co Ltd | Impeller for centrifugal pump and centrifugal pump having the same |
Also Published As
| Publication number | Publication date |
|---|---|
| CA2731127A1 (en) | 2010-01-21 |
| JPWO2010007780A1 (en) | 2012-01-05 |
| US20110164968A1 (en) | 2011-07-07 |
| WO2010007780A1 (en) | 2010-01-21 |
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Application publication date: 20110615 |