CN1648463A - Radial impeller - Google Patents
Radial impeller Download PDFInfo
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- CN1648463A CN1648463A CN 200510007008 CN200510007008A CN1648463A CN 1648463 A CN1648463 A CN 1648463A CN 200510007008 CN200510007008 CN 200510007008 CN 200510007008 A CN200510007008 A CN 200510007008A CN 1648463 A CN1648463 A CN 1648463A
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- Prior art keywords
- impeller
- blade
- receded disk
- side plate
- mainboard
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Abstract
The invention provided a radial impeller, simplifying a metal mold for mass-production of a radial impeller to heighten the production efficiency while attaining high efficiency of the radial impeller of a centrifugal fluid machine and realizing a low-noise pump. In the centrifugal fluid machine such as a centrifugal pump, the radial impeller is so constructed that a blade pressure surface 6 of the radial impeller 1 is shaped like a two-dimensional curved surface, a blade negative pressure surface 7 is shaped like a three-dimensional curved surface, the blade thickness 19 of the impeller hub 3 side is made larger than the blade thickness 19 of an impeller rear face shroud 5 side, and the blade thickness 19 is gradually decreased as it goes from the impeller hub 3 side toward the impeller rear face shroud 5 side, thereby gradually decreasing the blade inlet angle 16 of the radial impeller 1 as it goes from the impeller hub 3 side toward the impeller rear face shroud 5 side.
Description
Technical field
The invention relates to the invention of the shape structure of the receded disk impeller in the centrifugal type fluid machine that comprises centrifugal pump, the particularly invention of constructing about the shape of the receded disk impeller in the centrifugal pump.
Background technique
Receded disk impeller 1 for the centrifugal pump of in Fig. 1, representing, the same as what represent among Fig. 4 and Fig. 5, in order fluid can be flow through swimmingly guaranteed since the interlobate runner 10 receded disk impeller 1 can realize high efficiency, make the consistent no conflict of guaranteeing blade 4 of inlet blade angle 16 and fluid inlet corner 17 flow into condition and the collision loss that reduce in the interlobate runner 10 are very important.
In addition, consider general centrifugal pump performance, from impeller mainboard 3 sides to impeller side plate 5 sides, gradually the radius that increases the blade import 11 of receded disk impeller 1 is necessary, and on this basis, to impeller side plate 5 sides, must be designed to the inlet blade angle 16 of receded disk impeller 1 more and more littler from impeller mainboard 3 sides.Just because of this, represent in Fig. 4 and Fig. 5 that on the direction of blade height 18, the blade pressure surface 6 of most of adopted receded disk impellers 1 and blade suction surface 7 all are twisted into the ternary curve form simultaneously.
; when producing blade 4 in batches and be twisted into the receded disk impeller 1 of ternary curve form; particularly for the batch process of resinousness impeller; because on the direction of blade height 18, the blade 4 of receded disk impeller 1 is twisted into the ternary curve form, receded disk impeller 1 exists the problem of depanning difficulty from the mould of producing in batches; therefore; when batch process blade 4 was twisted into the receded disk impeller 1 of ternary curve form, it is complicated that the structure of mould becomes, and manufacturing efficiency has to reduce.
Simultaneously, for former receded disk impeller 1, particularly for the resinousness impeller, in order to solve the problem of receded disk impeller 1 depanning difficulty from the mould of producing in batches, represent that in Fig. 5 the blade pressure surface 6 of most receded disk impeller 1 and blade suction surface 7 all are designed to the shape of binary curved surface simultaneously.; blade 4 for the shape of such binary curved surface; because the inlet blade angle 16 and the fluid inlet corner 17 of receded disk impeller 1 become inconsistent; caused the fluid of blade 4 to flow into very big loss occurrence in collision loss and the vane channel 10, and made the receded disk impeller 1 of blade 4 of the shape of binary curved surface be difficult to realize high efficiency.
[patent documentation 1]
Patent application 2002-119764[2003 April 22 applied for (Japan)]
[non-patent literature 1]
" turbomachinery ", the 31st volume, No. 10 (in October, 2003 number), and the 22-28 page or leaf, Japanese industry is published
Summary of the invention
[problem to be solved by this invention]
Problem to be solved by this invention will provide and can realize high efficiency, and simplified the mould of producing in batches and enhanced productivity, and, reduced the receded disk impeller of the noise of centrifugal pump.
[technical solution]
In order fluid can be flow through swimmingly guaranteed since the interlobate runner 10 of receded disk impeller 1 receded disk impeller 1 to realize high efficiency, make the consistent no conflict of guaranteeing blade 4 of inlet blade angle 16 and fluid inlet corner 17 flow into condition and the collision loss that reduce in the vane channel 10 are very important.
Just because of this, in order to solve above problem, as method of the present invention, in the centrifugal type fluid machine that adopts receded disk impeller, for example in centrifugal pump, the blade pressure surface 6 of receded disk impeller 1 is with the binary curve form, impeller suction surface 7 constitutes with the ternary curve form, and, compare with the vane thickness 19 of impeller side plate 5 sides, when strengthening the vane thickness 19 of impeller mainboard 3 sides, to impeller side plate 5 sides, reduce the vane thickness 19 of impeller gradually, from impeller mainboard 3 sides with this, make inlet blade angle 16 become more and more littler, have the receded disk impeller 1 in the centrifugal type fluid machine of above feature from impeller mainboard 3 sides to impeller side plate 5 sides.
In addition, if the entrance radius of blade of impeller side plate 5 sides is r1s, the exit radius of blade of impeller side plate 5 sides is r2s, in the scope of blade 4 radiuses, to impeller side plate 5 sides, reduce the vane thickness 19 of impeller gradually from impeller mainboard 3 sides less than r1s+ (r2s-r1s) 2/3, with this, make the inlet blade angle 16 become more and more littler, have above feature, in the above Ji Zai receded disk impeller 1 from impeller mainboard 3 sides to impeller side plate 5 sides.
In addition, receded disk impeller 1 is the half-opened impeller that does not have impeller side plate 5 by having only impeller mainboard 3, perhaps, and the impeller mainboard 3 that only is reduced and do not have the full-open type impeller of impeller side plate 5 to constitute, has above feature, in the above Ji Zai receded disk impeller 1.
According to above method, receded disk impeller 1 can be realized high efficiency and low noise, and, because receded disk impeller 1 has become the easy shape of depanning from the mould of producing in batches is arranged, thereby can simplify the mould of the batch process usefulness of receded disk impeller 1, and improve the manufacturing efficiency of receded disk impeller 1.
[effect of invention]
The same just as described above, the centrifugal type fluid machine of the impeller that all constitutes with the ternary curve form with blade pressure surface and blade suction surface is compared, adopt blade pressure surface 6 of the present invention with the binary curve form, the receded disk impeller 1 that impeller suction surface 7 constitutes with the ternary curve form, neither can reduce the total efficiency of fluid machinery, again because the easy shape of depanning from the mould of producing in batches is arranged because receded disk impeller 1 has become, from and can simplify the mould of the batch process usefulness of receded disk impeller 1, and improve the manufacturing efficiency of receded disk impeller 1.Therefore, the present invention has significant invention effect.
Description of drawings
[Fig. 1]
(a) be the profile of sectional view, (b) be the front elevation of the sectional view of centrifugal pump with centrifugal pump of receded disk impeller.
[Fig. 2]
Fig. 2 is the ideograph of explanation receded disk impeller 1 structure of the present invention, (a) is the ideograph of the side view of impeller, (b) is the ideograph of the front shape of impeller.
[Fig. 3]
Fig. 3 is a part of sectional view of the receded disk impeller of other examples, (a) is a part of sectional view of the centrifugal pump of half-opened impeller, (b) a part of sectional view of the centrifugal pump of formula full-open type impeller.
[Fig. 4]
Fig. 4 is the leg-of-mutton explanatory drawing of blade inlet velocity.
[Fig. 5]
Fig. 5 is the ideograph of the receded disk impeller structure of ternary curve form before the explanation, (a) is the ideograph of the side view of impeller, (b) is the ideograph of the front shape of impeller.
[Fig. 6]
Fig. 6 is the ideograph of the receded disk impeller structure of binary curve form before the explanation, (a) is the ideograph of the side view of impeller, (b) is the ideograph of the front shape of impeller.
[Fig. 7]
Fig. 7 is the centrifugal pump performance comparison diagram that has the centrifugal pump of receded disk impeller 1 of the present invention and have the receded disk impeller of former ternary curve form, is expression flow Q, the graph of a relation of the input power of lift H and pump.
[Fig. 8]
Fig. 8 is the centrifugal pump performance comparison diagram that has the centrifugal pump of receded disk impeller 1 of the present invention and have the receded disk impeller of former ternary curve form, is the graph of a relation of the efficient of expression flow Q and pump.
[Fig. 9]
Fig. 9 has the centrifugal pump of receded disk impeller 1 of the present invention and the noise comparison diagram of the centrifugal pump of the receded disk impeller with former ternary curve form, is the graph of a relation of the level of noise of expression flow and pump.
Embodiment
With reference to accompanying drawing, carry out following explanation to implementing optimal morphology of the present invention.About accompanying drawing, Fig. 1 is the sectional view with centrifugal pump of receded disk impeller.Fig. 2 is a kind of ideograph of implementing the structural form of receded disk impeller 1 of the present invention of explanation.Fig. 3 is a part of sectional view of the receded disk impeller of other examples.Fig. 4 is the leg-of-mutton explanatory drawing of blade inlet velocity.Fig. 5 is the ideograph of the receded disk impeller structure of ternary curve form before the explanation.Fig. 6 is the ideograph of the receded disk impeller structure of binary curve form before the explanation.Fig. 7 is the centrifugal pump performance comparison diagram that has the centrifugal pump of receded disk impeller 1 of the present invention and have the receded disk impeller of former ternary curve form, is expression flow Q, the graph of a relation of the input power of lift H and pump.Fig. 8 is the centrifugal pump performance comparison diagram that has the centrifugal pump of receded disk impeller 1 of the present invention and have the receded disk impeller of former ternary curve form, is the graph of a relation of the efficient of expression flow and pump.Fig. 9 has the centrifugal pump of receded disk impeller 1 of the present invention and the noise comparison diagram of the centrifugal pump of the receded disk impeller with former ternary curve form.
The present invention is an example with the centrifugal pump of a kind of example of centrifugal type fluid machine, with reference to Fig. 1, on volute 20, the pump inlet 8 of inhalant liquid body and function and the pump discharge 9 that ejection liquid is used is arranged, and in volute 20, volute chamber 2 is arranged.Receded disk impeller 1 by driven by motor is assemblied in the volute chamber 2 just.Along with the rotation of receded disk impeller 1, liquid is sucked into volute chamber 2 through blade import 11, then again from the blade exit 12 of the periphery of volute chamber 2 through pump discharges 9 ejections.In this centrifugal pump, in Fig. 2, represent, blade import mainboard side radius 13 is arranged in the blade import 11 of receded disk impeller 1, blade import intermediate portion radius 14 and blade import side plate side radius 15, the blade pressure surface 6 of blade 4 is with the binary curve form, blade suction surface 7 constitutes with the ternary curve form, and, compare with the vane thickness 19 of impeller side plate 5 sides, when strengthening the vane thickness 19 of impeller mainboard 3 sides, to impeller side plate 5 sides, reduce the vane thickness 19 of impeller gradually from impeller mainboard 3 sides, with this, make inlet blade angle 16 become more and more littler from impeller mainboard 3 sides to impeller side plate 5 sides.
In addition, centrifugal pump for other examples of centrifugal type fluid machine of the present invention, if the blade import of impeller side plate 5 sides 11 radiuses 15 are r1s, the blade exit 12 of impeller side plate 5 sides is that blade exit side plate side radius 21 is r2s, in the scope of blade radius, to impeller side plate 5 sides, reduce the vane thickness 19 of impeller gradually from impeller mainboard 3 sides less than r1s+ (r2s-r1s) 2/3, with this, make inlet blade angle 16 become more and more littler from impeller mainboard 3 sides to impeller side plate 5 sides.
In addition, receded disk impeller 1 for the centrifugal pump of other examples of centrifugal type fluid machine of the present invention, in Fig. 3 (a), represent, be to have only impeller mainboard 3 and the half-opened impeller 1 that do not have impeller side plate 5, perhaps, expression in Fig. 3 (b) is the impeller mainboard 3 that only is reduced and do not have the receded disk impeller 1 of the full-open type impeller formation of impeller side plate 5.This half-opened impeller 1 or full-open type impeller 1 mainly are to handle the receded disk impeller of using centrifugal pump as the suspension of solid or fiber or the like, compare with the centrifugal pump of impeller side plate 5 with having long mainboard 3, the suspension of solid or fiber or the like is not easy to stop up.
Because receded disk impeller 1 has become above-mentioned shape, make receded disk impeller 1 depanning from the mould of producing in batches easy, therefore, can simplify the mould of the batch process usefulness of receded disk impeller 1, improve the manufacturing efficiency of receded disk impeller 1, simultaneously, owing to can make inlet blade angle 16 consistent, can improve the efficient of receded disk impeller 1 again again with fluid inlet corner 17.
As the receded disk impeller 1 of centrifugal pump, a kind of is impeller 1 of the present invention, and the blade pressure surface 6 that is blade 4 is with the binary curve form, and blade suction surface 7 is with the receded disk impeller 1 of ternary curve form formation.Another kind is a former receded disk impeller 1, is the receded disk impeller 1 that blade pressure surface 6 and blade suction surface 7 all constitute with the ternary curve form simultaneously.Though the blade shape difference of these two kinds of receded disk impellers 1,, other condition is all the same.Fig. 2 is the sectional view of receded disk impeller 1 structure of the present invention.Fig. 5 is the sectional view of the receded disk impeller structure of former ternary curve form.
[embodiment]
As the embodiment of receded disk impeller 1 of the present invention, the major parameter of receded disk impeller 1 is as follows.
The diameter of receded disk impeller 1 is φ 127.0mm, the blade angle of blade exit 12 is 25.00 °, the blade height 18 of blade exit 12 is 11.0mm, the vane thickness 19 of blade exit 12 is 5.0mm, the inlet blade angle of the mainboard side of blade import 11 is 33.34 °, the inlet blade angle of the intermediate portion of blade import 11 is 26.61 °, the inlet blade angle of the side plate side of blade import 11 is 21.00 °, blade import mainboard side radius 13 is 23.0mm, the radius 14 of blade import intermediate portion is 27.7mm, blade import side plate side radius 15 is 32.5mm, and the number of blade is 5 pieces.
Fig. 7 has the centrifugal pump of receded disk impeller 1 of the present invention and has the centrifugal water-test performance of the pump comparison diagram of the receded disk impeller of former ternary curve form, is to represent flow Q[L/min], lift H[m] and the graph of a relation of the input power [W] of pump.Fig. 8 is the centrifugal water-test performance of the pump comparison diagram that has the centrifugal pump of receded disk impeller 1 of the present invention and have the receded disk impeller of former ternary curve form, is the graph of a relation of the efficient [%] of expression flow [L/min] and pump.Compare with the total efficiency of the centrifugal pump of the receded disk impeller of former ternary curve form, the centrifugal pump of receded disk impeller 1 of the present invention almost reaches identical total efficiency, and this explanation receded disk impeller 1 of the present invention also can be realized high efficiency.And for example go up saidly, depanning is easy to shape from the mould of producing in batches because receded disk impeller 1 of the present invention has, and the mould of the batch process usefulness of receded disk impeller 1 can obtain simplifying, and has improved the manufacturing efficiency of receded disk impeller 1.
Fig. 9 has the centrifugal pump of receded disk impeller 1 of the present invention and the noise comparison diagram of the centrifugal pump of the receded disk impeller with former ternary curve form.It is the graph of a relation of expression flow [L/min] and actual measurement noise [dB].As seen from the figure, compare, adopt the noise of the centrifugal pump of receded disk impeller 1 of the present invention to obtain significantly reducing with the noise of the centrifugal pump of the receded disk impeller of former ternary curve form.
Claims (3)
1. the receded disk impeller in the centrifugal type fluid machine, it is characterized in that, in the centrifugal type fluid machine that adopts receded disk impeller, the blade pressure surface of receded disk impeller is with the binary curve form, the impeller suction surface constitutes with the ternary curve form, and, compare with the vane thickness of impeller side plate side, when strengthening the vane thickness of impeller mainboard side, from the impeller mainboard side to impeller side plate side, gradually reduce the vane thickness of impeller,, make inlet blade angle become more and more littler from the impeller mainboard side to impeller side plate side with this.
2. receded disk impeller according to claim 1, it is characterized in that, if the entrance radius of blade of impeller side plate side is r1s, the exit radius of blade of impeller side plate side is r2s, in the scope of blade radius, to impeller side plate side, reduce the vane thickness of impeller gradually from the impeller mainboard side less than r1s+ (r2s-r1s) 2/3, with this, make inlet blade angle become more and more littler from the impeller mainboard side to impeller side plate side.
3. receded disk impeller according to claim 1 and 2 is characterized in that, receded disk impeller is the half-opened impeller that does not have the impeller side plate by having only the impeller mainboard, perhaps, and the impeller mainboard that only is reduced and do not have the full-open type impeller of impeller side plate to constitute.
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2004-021783 | 2004-01-29 | ||
| JP2004021783 | 2004-01-29 | ||
| JP2004021783A JP3949663B2 (en) | 2004-01-29 | 2004-01-29 | Centrifugal impeller |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN1648463A true CN1648463A (en) | 2005-08-03 |
| CN100434723C CN100434723C (en) | 2008-11-19 |
Family
ID=34056300
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CNB2005100070081A Active CN100434723C (en) | 2004-01-29 | 2005-01-31 | Radial impeller |
Country Status (2)
| Country | Link |
|---|---|
| JP (1) | JP3949663B2 (en) |
| CN (1) | CN100434723C (en) |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN107448412A (en) * | 2016-06-01 | 2017-12-08 | 株式会社久保田 | Impeller |
| CN107448413A (en) * | 2016-06-01 | 2017-12-08 | 株式会社久保田 | Impeller |
| CN108468654A (en) * | 2018-04-09 | 2018-08-31 | 张家港市海工船舶机械制造有限公司 | A kind of half-opened impeller and its manufacturing method |
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| DE102008054587A1 (en) * | 2008-12-12 | 2010-06-17 | Basf Se | Process for the cleavage of Michael adducts contained in a liquid F, which was formed during the production of acrylic acid or its esters |
| WO2012033495A1 (en) * | 2010-09-10 | 2012-03-15 | Pratt & Whitney Rocketdyne, Inc. | Pumping element design |
| US10137264B2 (en) | 2011-07-13 | 2018-11-27 | Fisher & Paykel Healthcare Limited | Respiratory assistance apparatus |
| CA3056453C (en) | 2011-07-13 | 2023-08-22 | Fisher & Paykel Healthcare Limited | Impeller and motor assembly |
| EP2809383B1 (en) * | 2012-02-02 | 2021-04-07 | Fisher&Paykel Healthcare Limited | Respiratory assistance apparatus |
| AU2013365897A1 (en) | 2012-12-18 | 2015-07-16 | Fisher & Paykel Healthcare Limited | Impeller and motor assembly |
| JP2014145269A (en) * | 2013-01-28 | 2014-08-14 | Asmo Co Ltd | Vehicular pump device |
| CN103591046B (en) * | 2013-11-12 | 2016-06-15 | 大连理工大学 | A kind of high-power shield electric machine core main pump high-efficiency hydraulic model under multi-source constraint |
| CN104196731A (en) * | 2014-08-20 | 2014-12-10 | 江苏超力电器有限公司 | Brushless direct-current magnetic isolation type water pump |
| MX2017003271A (en) | 2017-03-03 | 2017-08-31 | Javier BUSTAMANTE SANDOVAL Francisco | Mechanism for the propulsion of centrifugal pump blades to transport liquids and live fauna. |
| SG11201909879QA (en) | 2017-04-23 | 2019-11-28 | Fisher & Paykel Healthcare Ltd | Breathing assistance apparatus |
| CN110909422B (en) * | 2019-10-22 | 2021-06-04 | 浙江理工大学 | Method for predicting and optimizing range of efficient working condition area of centrifugal pump impeller |
| US11805765B1 (en) | 2023-02-07 | 2023-11-07 | Bradley Toschlog | Centrifugal pump system |
Family Cites Families (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2661986B2 (en) * | 1988-09-30 | 1997-10-08 | 松下冷機株式会社 | Centrifugal blower impeller |
| JPH0589893U (en) * | 1992-05-11 | 1993-12-07 | 株式会社川本製作所 | Centrifugal pump |
| JP2871515B2 (en) * | 1995-03-06 | 1999-03-17 | 松下冷機株式会社 | Centrifugal blower |
-
2004
- 2004-01-29 JP JP2004021783A patent/JP3949663B2/en not_active Expired - Lifetime
-
2005
- 2005-01-31 CN CNB2005100070081A patent/CN100434723C/en active Active
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN107448412A (en) * | 2016-06-01 | 2017-12-08 | 株式会社久保田 | Impeller |
| CN107448413A (en) * | 2016-06-01 | 2017-12-08 | 株式会社久保田 | Impeller |
| CN108468654A (en) * | 2018-04-09 | 2018-08-31 | 张家港市海工船舶机械制造有限公司 | A kind of half-opened impeller and its manufacturing method |
Also Published As
| Publication number | Publication date |
|---|---|
| JP3949663B2 (en) | 2007-07-25 |
| CN100434723C (en) | 2008-11-19 |
| JP2004353655A (en) | 2004-12-16 |
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