CN108843619A - A kind of double-volute structure of centrifugal pump - Google Patents
A kind of double-volute structure of centrifugal pump Download PDFInfo
- Publication number
- CN108843619A CN108843619A CN201810690428.1A CN201810690428A CN108843619A CN 108843619 A CN108843619 A CN 108843619A CN 201810690428 A CN201810690428 A CN 201810690428A CN 108843619 A CN108843619 A CN 108843619A
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- China
- Prior art keywords
- partition
- volute
- double
- spiral case
- centrifugal pump
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- 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.)
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Classifications
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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
- F04D29/40—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
- F04D29/007—Details, component parts, or accessories 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
- F04D29/40—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
- F04D29/428—Discharge tongues
-
- 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
- F04D29/4293—Details of fluid inlet or outlet
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Structures Of Non-Positive Displacement Pumps (AREA)
Abstract
The present invention relates to field of fluid machinery, more particularly to a kind of double-volute structure of centrifugal pump, cut water is equipped with including spiral case, the volute casing in spiral case and the diffuser at volute outlet, spiral case and diffuser contact position, partition is equipped in spiral case, volute casing is separated into two volute passages by partition, the head end of partition is wedge angle, and the trailing edge of partition is wedge angle.The wedge angle of partition head end eliminate due to the presence of cut water make the distribution of two runner forefront pressures generate very big differences so as to cause impeller force in radial increase the drawbacks of, it is serious in partition trailing edge flow losses that the wedge angle of partition trailing edge overcomes traditional double volute, there is a phenomenon where flow separations, the lift of fluid is improved, to improve efficiency.
Description
Technical field
The present invention relates to field of fluid machinery, more particularly to a kind of double-volute structure applied to centrifugal pump.
Background technique
The spiral case form of current research is mostly conventional single spiral case, since double-volute structure can make pump internal flow more right
Claim, radial force is compared to single volute structure and greatly weakens, and the operation of pump is more stable, thus application is relatively broad.
Double volute form is arranged symmetrically by two individual runners, and the sum of two symmetrical throat opening areas are equal to single spiral case
Throat opening area.Double volute has a following characteristics, radial force kept in balance, and pump operation is steady；The efficiency of double volute pump and single snail
Shell phase is close, and in optimum operating condition l%~1.5% lower than single spiral case, about higher by 2% than single spiral case in off-design behaviour, higher efficiency range is wide；
For double volute due to being double-layer channel, casting is difficult, in the case where flow is less than 90mVh, should not use double volute runner, be suitably applied
Under conditions of big flow.
Centrifugal pump can generate radial force, for pump shaft, radial force when running under deviateing design conditions and zero delivery
It is an alternating load, will cause the vibration of pump shaft when the radial force of generation is excessive, so as to cause the vibration of pump, increasing pump
Unstability.So the balance of the radial force of centrifugal pump is very important, the especially pump to the high lift of big flow.Conventional
Double volute can theoretically balance radial force well, but due to the presence of cut water and the asymmetric pump housing, it is practical
Upper double volute can not complete equipilibrium radial force.For the pump of the high lift of big flow, it is being lower than metered flow operating condition
Under even with double-volute structure, impeller force in radial is still larger.Under design conditions, theoretical upper fluid is having around impeller
Speed in pumping chamber with pressure be it is uniform, symmetrical, pretending with the resultant force on impeller is zero.But in fact, spiral case every
Tongue attachment there are fluid impact, can stream field form disturbance, the radial force that impeller is subject to be not be zero.When centrifugal pump is inclined
When from running under the conditions of design discharge, scroll casing shape line, which goes out the streamline flowed with practical impeller, to be deviateed, and causes the speed of impeller periphery
Degree and pressure are uneven, mal-distribution, and it is bigger to deviate design discharge, the speed and pressure of this impeller periphery it is uneven with
Asymmetric more serious, the radial force showed is higher.Double volute can be by being divided into two for runner, that is, spiral case of impeller outer
Scroll casing shape eliminates radial force at symmetrical structure, but this does not consider influence of the special construction to radial force of cut water, and cut water exists
The front end in first channel, being distributed there are two runner forefront pressures for cut water generate very big differences, and impeller force in radial increases
Greatly.
Summary of the invention
The purpose of the present invention is to provide a kind of double-volute structures of centrifugal pump, to overcome double volute impeller in the prior art
The big problem of force in radial.
The present invention is to be achieved through the following technical solutions：
A kind of double-volute structure of centrifugal pump, including spiral case, the volute casing in spiral case and the expansion at volute outlet
Equipped with partition is equipped in cut water, spiral case, volute casing is separated into two volute passages by partition for separate tube, spiral case and diffuser contact position,
Partition is trailing edge close to the side of diffuser, and the other side is head end, and the head end of partition is tip-angled shape, and the pointed peak is located at snail
On the middle section of shell.
Further, the pointed peak of the head end of partition and cut water are symmetrical about the basic circle center of circle of spiral case.
Further, the trailing edge of partition is tip-angled shape, and pointed peak is located on the middle section of spiral case.
Further, wedge angle angle is acute angle.
Further, the wedge angle size of the head end of partition is 50 °~60 °.
Further, the wedge angle size of the trailing edge of partition is 40 °~50 °.
Further, wedge angle with a thickness of the 1/2 of partition maximum gauge.
Further, the roughness of partition is Ra<6.3μm.
Compared with prior art, the invention has the following beneficial technical effects：
The present invention can eliminate the presence due to cut water in the wedge angle of partition first section setting certain angle to a certain extent
Make the distribution of two runner forefront pressures generate very big differences so as to cause impeller force in radial increase the drawbacks of so that partition
Nearby flow field is even more like with partition in head end flow field, so that entire Scroll's flow field is more symmetrical；Certain angle of partition trailing edge setting
The wedge angle of degree can be good at the impact loss and flow losses in basin where reducing, improve the characteristic curve of centrifugal pump, mention
High flow lift and efficiency.Present invention can apply to big flow high-lift centrifugal pumps.
Detailed description of the invention
Fig. 1 is a kind of structural schematic diagram of centrifugal pump double volute provided by the invention；
Fig. 2 be a kind of radial force of centrifugal pump double volute provided by the invention under head end cut water wedge angle different angle with stream
The relationship of amount；
Fig. 3 a and 3b are the centrifugal pump double volute and only head that first section provided by the invention and trailing edge are all tip-angled shape respectively
Section is motion pattern of the double volute of tip-angled shape on middle section；
Fig. 4 is a kind of lift of the double volute of centrifugal pump provided by the invention in trailing edge cut water wedge angle different angle and flows
The relationship of amount；
Fig. 5 is that same centrifugal pump is schemed using the efficiency comparative of double-volute structure and traditional double volute of the invention；
Fig. 6 is fluid lift comparison diagram of the same centrifugal pump using double-volute structure and traditional double volute of the invention；
Fig. 7 is that same centrifugal pump uses average radial suffered by the double volute of centrifugal pump of the present invention and traditional double volute impeller
The comparison diagram of power.
Wherein, 1- volute casing, 2- cut water, 3- partition, 4- diffuser, 5- spiral case.
Specific embodiment
Below with reference to specific embodiment, the present invention is described in further detail, it is described be explanation of the invention and
It is not to limit.
As shown in FIG. 1, FIG. 1 is a kind of double-volute structure schematic diagrames applied to centrifugal pump, including spiral case 5, are set to spiral case 5
Be equipped at interior volute casing 1 and the diffuser 4 set on 5 exit of spiral case, 5 upper end of spiral case and diffuser 4 and 5 upper-end contact of spiral case every
Tongue 2, spiral case 5 is interior to be equipped with partition 3, and volute casing 1 is separated into two volute passages by partition 3, and the head end of partition 3 is wedge angle, partition 3
Pointed peak, cut water 2 and the 5 basic circle center of circle of spiral case of head end are on same straight line；The trailing edge of partition 3 is wedge angle, the tail of partition 3
Point-blank, the head end of partition 3 is that wedge angle size is 50 °~60 ° to the pointed peak and cut water 2 of edge, and the trailing edge of partition 3 is
Wedge angle size is 40 °~50 °.
Referring to fig. 2, for a kind of centrifugal pump double volute in impeller radial force in head end cut water wedge angle different angle with
The relationship of flow.It can be seen from the figure that when flow is identical, the radial force of impeller 3 head end wedge angle angle of partition be 30 °,
It is in reduction trend at 40 ° and 50 °, being 50 °, 60 ° and 70 ° in 3 head end wedge angle angle of partition has the tendency that increase, reaches when to 50 °
To minimum value, again as can be seen that the radial force of impeller, which is 60 ° in 3 head end wedge angle angle of partition, is lower than 40 °, so leaf from figure
The minimum of the radial force of wheel obtains between 50 ° -60 °.Fig. 2 is also illustrated can by 3 head end of sharpening partition in the present invention
Eliminate to a certain extent due to the presence of cut water 2 make the distribution of two runner forefront pressures generate very big differences so as to cause leaf
Take turns the drawbacks of force in radial increases.
Referring to Fig. 3, Fig. 3 a and 3b are the streamline of centrifugal pump double volute of the present invention and traditional double volute on middle section respectively
Flow separation occurs for figure, or even generate whirlpool from Fig. 3 (b) as can be seen that traditional double volute is serious in partition trailing edge flow losses
Rotation；It is angled by the way that 3 trailing edge of partition is done, flow field herein is improved, unnecessary flow losses are reduced, from Fig. 3
(b) as can be seen that partition trailing edge flow losses it is serious, generate flow separation the phenomenon that be obviously improved.
Referring to fig. 4, Fig. 4 is a kind of lift of centrifugal pump double volute provided by the invention in trailing edge cut water wedge angle different angle
When and flow relationship, it can be seen from the figure that when flow is identical, tail of the fluid lift in partition 3 in centrifugal pump double volute
Edge wedge angle angle reaches maximum when being 40 ° -50 °.This illustrates effectively reduce in the present invention using the trailing edge of sharpening partition 3
Flow losses, and fluid lift can be improved for 40 ° -50 ° by the trailing edge wedge angle angle of setting partition 3 to the greatest extent.
Referring to Fig. 5,6 and 7, Fig. 5,6 and 7 are respectively same centrifugal pump using the improved centrifugal pump double volute of the present invention and pass
The comparison diagram for average radial power suffered by efficiency, lift and the impeller of double volute of uniting；It is double using centrifugal pump through Simulation
Compared with using traditional double volute, radial force and hydraulic performance have to be obviously improved spiral case, in terms of hydraulic performance, small flow
Under lower and metered flow, the two is without significant difference, but under big flow, improvement due to partition trailing edge wedge angle to flowing is centrifuged
Efficiency and the lift for pumping double volute pump are higher than traditional double volute；In terms of radial force, due to the presence of partition head end wedge angle, centrifugation
Pump double volute impeller of pump force in radial is significantly less than traditional double volute pump.It can be seen that the double snails of centrifugal pump provided by the invention
Shell solves the deficiency of traditional double-volute structure, improves radial force suffered by impeller, and under conditions of big flow, improves
Efficiency.
Claims (8)
1. a kind of double-volute structure of centrifugal pump, which is characterized in that including spiral case (5), be set to spiral case (5) in volute casing (1) and
Cut water (2) are equipped with set on the diffuser (4) in spiral case (5) exit, spiral case (5) and diffuser (4) contact position, are set in spiral case (5)
Have partition (3), volute casing (1) is separated into two volute passages by partition (3), and partition (3) is tail close to the side of diffuser (4)
Edge, the other side are head end, and the head end of partition (3) is tip-angled shape, and the pointed peak is located on the middle section of spiral case (5).
2. the double-volute structure of centrifugal pump according to claim 1, which is characterized in that the wedge angle top of the head end of partition (3)
Point is symmetrical about the basic circle center of circle of spiral case (5) with cut water (2).
3. the double-volute structure of centrifugal pump according to claim 1, which is characterized in that the trailing edge of partition (3) is tip-angled shape,
Pointed peak is located on the middle section of spiral case (5).
4. the double-volute structure of centrifugal pump according to claim 2 or 3, which is characterized in that wedge angle angle is acute angle.
5. the double-volute structure of centrifugal pump according to claim 1 or 2, which is characterized in that the wedge angle of the head end of partition (3)
Size is 50 °~60 °.
6. the double-volute structure of centrifugal pump according to claim 3, which is characterized in that the wedge angle of the trailing edge of partition (3) is big
Small is 40 °~50 °.
7. the double-volute structure of centrifugal pump according to claim 2 or 3, which is characterized in that wedge angle with a thickness of partition (3)
The 1/2 of maximum gauge.
8. the double-volute structure of centrifugal pump according to claim 1-3, which is characterized in that partition (3) it is coarse
Degree is Ra<6.3μm.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201810690428.1A CN108843619B (en) | 2018-06-28 | 2018-06-28 | Double-volute structure of centrifugal pump |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201810690428.1A CN108843619B (en) | 2018-06-28 | 2018-06-28 | Double-volute structure of centrifugal pump |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN108843619A true CN108843619A (en) | 2018-11-20 |
| CN108843619B CN108843619B (en) | 2020-05-22 |
Family
ID=64200815
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201810690428.1A Active CN108843619B (en) | 2018-06-28 | 2018-06-28 | Double-volute structure of centrifugal pump |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN108843619B (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN112696356A (en) * | 2020-12-14 | 2021-04-23 | 江苏大学 | Centrifugal pump with equivalent shunting volute and detachable shunting blades |
Citations (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US1390391A (en) * | 1920-01-12 | 1921-09-13 | Jr Benjamin Skidmore | Fluid-pump |
| US5332359A (en) * | 1993-10-12 | 1994-07-26 | United Technologies Corporation | Stator assembly for a rotary machine having a centrifugal on impeller and volute |
| JPH11166499A (en) * | 1997-12-03 | 1999-06-22 | Torishima Pump Mfg Co Ltd | Centrifugal pump |
| US6146095A (en) * | 1997-09-15 | 2000-11-14 | Ksb Aktiengesellschaft | Spiral housing pump |
| CN101668954A (en) * | 2007-05-11 | 2010-03-10 | 三菱重工业株式会社 | Centrifugal blower |
| US20120253103A1 (en) * | 2011-03-30 | 2012-10-04 | Robert Jarvik Md | Centrifugal blood pumps with reverse flow washout |
| CN102869889A (en) * | 2010-05-07 | 2013-01-09 | 苏舍泵有限公司 | Volute shaped pump casing with splitter rib |
| CN106438483A (en) * | 2016-10-19 | 2017-02-22 | 广东肯富来泵业股份有限公司 | Double-volute centrifugal pump |
-
2018
- 2018-06-28 CN CN201810690428.1A patent/CN108843619B/en active Active
Patent Citations (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US1390391A (en) * | 1920-01-12 | 1921-09-13 | Jr Benjamin Skidmore | Fluid-pump |
| US5332359A (en) * | 1993-10-12 | 1994-07-26 | United Technologies Corporation | Stator assembly for a rotary machine having a centrifugal on impeller and volute |
| US6146095A (en) * | 1997-09-15 | 2000-11-14 | Ksb Aktiengesellschaft | Spiral housing pump |
| JPH11166499A (en) * | 1997-12-03 | 1999-06-22 | Torishima Pump Mfg Co Ltd | Centrifugal pump |
| CN101668954A (en) * | 2007-05-11 | 2010-03-10 | 三菱重工业株式会社 | Centrifugal blower |
| CN102869889A (en) * | 2010-05-07 | 2013-01-09 | 苏舍泵有限公司 | Volute shaped pump casing with splitter rib |
| US20120253103A1 (en) * | 2011-03-30 | 2012-10-04 | Robert Jarvik Md | Centrifugal blood pumps with reverse flow washout |
| CN106438483A (en) * | 2016-10-19 | 2017-02-22 | 广东肯富来泵业股份有限公司 | Double-volute centrifugal pump |
Non-Patent Citations (2)
| Title |
|---|
| 段海发: "《输油设备》", 30 April 1989 * |
| 钱锡俊等: "《泵和压缩机》", 30 September 1994 * |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN112696356A (en) * | 2020-12-14 | 2021-04-23 | 江苏大学 | Centrifugal pump with equivalent shunting volute and detachable shunting blades |
| CN112696356B (en) * | 2020-12-14 | 2022-05-20 | 江苏大学 | Centrifugal pump with equivalent shunting spiral case and detachable shunting blades |
Also Published As
| Publication number | Publication date |
|---|---|
| CN108843619B (en) | 2020-05-22 |
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