CN1815039A - Multi-stage centrifugal pump capable of self-balancing axial force by impeller - Google Patents
Multi-stage centrifugal pump capable of self-balancing axial force by impeller Download PDFInfo
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- CN1815039A CN1815039A CN 200610038596 CN200610038596A CN1815039A CN 1815039 A CN1815039 A CN 1815039A CN 200610038596 CN200610038596 CN 200610038596 CN 200610038596 A CN200610038596 A CN 200610038596A CN 1815039 A CN1815039 A CN 1815039A
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- impeller
- axial force
- centrifugal pump
- front shroud
- face seal
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- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 claims description 9
- 238000000034 method Methods 0.000 abstract description 8
- 230000006378 damage Effects 0.000 abstract description 4
- 238000004519 manufacturing process Methods 0.000 abstract description 4
- 230000000694 effects Effects 0.000 abstract description 2
- 238000007789 sealing Methods 0.000 abstract 1
- 239000012530 fluid Substances 0.000 description 2
- 239000000463 material Substances 0.000 description 2
- 230000006978 adaptation Effects 0.000 description 1
- 230000009286 beneficial effect Effects 0.000 description 1
- 230000007812 deficiency Effects 0.000 description 1
- 239000007788 liquid Substances 0.000 description 1
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Abstract
Said invention refers to multistage centrifugal pump with impeller self balancing axial force. Said invention adopts end surface sealed structure on impeller entrance, the impeller band being greater than impeller hub area, the fit between impeller band outside diameter with diversion shell being clearance fit, impeller entrance end surface sealing sub being thrust bearing sub etc method to realize completely balancing axial thrust effect depending on impeller itself, thoroughly solving multistage centrifugal pump axial force destruction problem, and reducing multistage centrifugal pump production costs.
Description
Affiliated technical field
The present invention is a kind of fluid machinery that is used for improving fluid pressure, and especially a kind of needs overcome the multistage centrifugal pump of axial force.
Background technique
At present, all there is serious axial force problem in known multistage centrifugal pump, because when impeller is worked, can produce axial force on impeller, and the impeller of multistage centrifugal pump is many, and its axial force problem is also just serious.General single stage centrifugal pump adopts the radial seal ring to add equalizing orifice on impeller or these two kinds of methods of back blade are come the balance portion axial force, the residue axial force is born by bearing, and multistage centrifugal pump generally adopts balancing drum or these two kinds of methods of Balance disc device to come balancing axial thrust.In these four kinds of methods, have only this method of Balance disc device automatically balancing axial force fully, other three kinds of methods all have the residue axial force, and concerning multistage centrifugal pump, the residue axial force is very big sometimes, therefore still have the possibility that causes damage.And Balance disc Design of device and manufacture difficulty are very big, because multistage centrifugal pump needs the axial force of balance very big in the startup instantaneous variation, so the Balance disc device has mistake slightly in design with in making, moving and the Balance disc friction of powerful rotor string will take place in the start-up course of pump, also can cause the damage of multistage centrifugal pump.
Summary of the invention
In order to overcome the deficiency of existing multistage centrifugal pump, the invention provides a kind of novel multistage centrifugal pump, it can rely on impeller self complete equilibrium axial force, improves the operational safety of multistage centrifugal pump and can reduce the cost of production of multistage centrifugal pump.
Technological scheme of the present invention is:
Connect in the multistage centrifugal pump that same inlet segment and water exit end be in series at the above impeller of two-stage and blower inlet casing, before employing has, the return guide vane blower inlet casing of back shroud and have before, the double shrouded wheel of back shroud, the external diameter of back shroud of impeller is less than the external diameter of front shroud of impeller, impeller inlet adopts end face seal, the impeller axis hole is a Spielpassung with cooperating of pump shaft, its innovation is: the area of front shroud of impeller is greater than the area of back shroud of impeller, the front shroud of impeller external diameter is a Spielpassung with cooperating of blower inlet casing, and the end face seal pair of impeller inlet is made the thrust-bearing pair that can bear small axial force.
The principle of its balancing axial thrust is, when the secondary closely contact of the end face seal of impeller inlet or gap are minimum, the end face seal of impeller inlet will be played fabulous seal action, the pressure (being pressure) of unit area will be not less than the pressure of unit area on the back shroud of impeller on this moment front shroud of impeller, again because the area of front shroud of impeller greater than the area of back shroud of impeller, so active force suffered on the front shroud of impeller will be greater than active force suffered on the back shroud of impeller, impeller will the direction along pump shaft towards back shroud of impeller move, the gap of impeller inlet end face seal pair is strengthened, make the flow direction impeller inlet at front shroud of impeller place, and the pressure that acts on the front shroud of impeller is reduced, till the axial force complete equilibrium on the impeller.If the gap of impeller inlet end face seal pair is very big, make the pressure (being pressure) of unit area on the front shroud of impeller be far smaller than the pressure of unit area on the back shroud of impeller, cause active force suffered on the front shroud of impeller less than active force suffered on the back shroud of impeller, impeller will the direction along pump shaft towards front shroud of impeller move, the gap of impeller inlet end face seal pair is reduced, till the axial force complete equilibrium on the impeller.
The front shroud of impeller external diameter adopts Spielpassung with cooperating of blower inlet casing, is ability and raising pump efficiency in order to increase impeller self balancing axial thrust.Because this gap can hinder the position that the liquid of impeller outlet flows to front shroud of impeller fast, so, the pressure that acts on the front shroud of impeller is reduced greatly and reach the purpose of complete equilibrium axial force as long as impeller inlet end face seal pair has very little gap.And the leakage that reduces the impeller inlet end face seal is exactly the volumetric efficiency that improves water pump.
The end face seal pair of impeller inlet is made the thrust-bearing pair that can bear small axial force, be because in the start-up course of pump, secondary closely contact of the end face seal of unavoidable impeller inlet and friction, but its axial force is the pressure difference and the inertial force of an impeller, so only need adopt the material that can bear small axial force just passable.
The invention has the beneficial effects as follows that the present invention can rely on impeller self complete equilibrium axial force, the axial force that has thoroughly solved multistage centrifugal pump is destroyed problem, and its manufacturing cost is all lower than other axial force balance method.
Description of drawings
The present invention is further described below in conjunction with drawings and Examples.
Fig. 1 is one embodiment of the present of invention.
Among the figure: 1. inlet segment, 2. pump shaft, 3. impeller axis hole, 4. blower inlet casing front shroud, 5. blower inlet casing, 6. blower inlet casing back shroud, 7. front shroud of impeller, 8. back shroud of impeller, 9. front shroud of impeller external diameter and blower inlet casing cooperates, 10. the stationary ring of impeller inlet end face seal, 11. the gap of impeller inlet end face seal pair, the rotating ring of 12. impeller inlet end face seals, 13. impellers, 14. the blower inlet casing stator, 15. water exit ends.
Embodiment
Embodiment illustrated in fig. 1 is a centrifugal pump for deep well, it also is a vertical multi-stage centrifugal pump, it connects same inlet segment (1) by three grades of impellers (13) and blower inlet casing (5) and a water exit end (15) is in series, blower inlet casing stator (14) is a return guide vane, its water inlet one side has blower inlet casing front shroud (4), water outlet simultaneously has blower inlet casing back shroud (6), impeller is the double shrouded wheel with front shroud of impeller (7) and back shroud of impeller (8), the external diameter of back shroud of impeller is less than the external diameter of front shroud of impeller, and the area of front shroud of impeller is greater than the area of back shroud of impeller, the front shroud of impeller external diameter is a Spielpassung with cooperate (9) of blower inlet casing, impeller inlet adopts end face seal, the impeller inlet end face seal pair of forming by the stationary ring (10) of the rotating ring (12) of impeller inlet end face seal and impeller inlet end face seal, its material and structural design have guaranteed that it also is the thrust-bearing pair that can bear small axial force simultaneously, impeller axis hole (3) is a Spielpassung with cooperating of pump shaft (2), impeller can be free vertically movable on pump shaft, and the gap (11) of impeller inlet end face seal pair changes size with the activity of impeller.
When present embodiment work started, impeller can be at pump shaft upper edge axial motion, when the rotating ring of impeller inlet end face seal and the stationary ring of impeller inlet end face seal are run into a time-out, because this also is the thrust-bearing pair to the end face seal pair, so can not damage to some extent.When present embodiment entered normal working, meeting adaptation condition in the gap of impeller inlet end face seal pair was adjusted to suitable size automatically, and axial force suffered on the impeller is equalled zero.Because when the secondary closely contact of the end face seal of impeller inlet or gap are minimum, the end face seal of impeller inlet will be played fabulous seal action, the pressure (being pressure) of unit area will be not less than the pressure of unit area on the back shroud of impeller on this moment front shroud of impeller, again because the area of front shroud of impeller greater than the area of back shroud of impeller, so active force suffered on the front shroud of impeller will be greater than active force suffered on the back shroud of impeller, impeller will the direction along pump shaft towards back shroud of impeller move, the gap of impeller inlet end face seal pair is strengthened, make the flow direction impeller inlet at front shroud of impeller place, and the pressure that acts on the front shroud of impeller is reduced, till the axial force complete equilibrium on the impeller.If the gap of impeller inlet end face seal pair is very big, make the pressure (being pressure) of unit area on the front shroud of impeller be far smaller than the pressure of unit area on the back shroud of impeller, cause active force suffered on the front shroud of impeller less than active force suffered on the back shroud of impeller, impeller will the direction along pump shaft towards front shroud of impeller move, the gap of impeller inlet end face seal pair is reduced, till the axial force complete equilibrium on the impeller.The front shroud of impeller external diameter adopts Spielpassung with cooperating of blower inlet casing, is ability and raising pump efficiency in order to increase impeller self balancing axial thrust.Because this gap can hinder the position that the press water of impeller outlet flows to front shroud of impeller fast, so, the pressure that acts on the front shroud of impeller is reduced greatly and reach the purpose of complete equilibrium axial force as long as impeller inlet end face seal pair has very little gap.And the leakage that reduces the impeller inlet end face seal is exactly the volumetric efficiency that improves water pump.
Claims (1)
1. the multistage centrifugal pump of impeller self balancing axial thrust, connect same inlet segment and a water exit end is in series by above impeller of two-stage and blower inlet casing, the blower inlet casing stator is before having, the return guide vane of back shroud, impeller is before having, the double shrouded wheel of back shroud, the external diameter of back shroud of impeller is less than the external diameter of front shroud of impeller, impeller inlet adopts end face seal, the impeller axis hole is a Spielpassung with cooperating of pump shaft, it is characterized in that: the area of front shroud of impeller is greater than the area of back shroud of impeller, the front shroud of impeller external diameter is a Spielpassung with cooperating of blower inlet casing, and the end face seal pair of impeller inlet is made the thrust-bearing pair that can bear small axial force.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CNB200610038596XA CN100365289C (en) | 2006-03-03 | 2006-03-03 | Multi-stage centrifugal pump capable of self-balancing axial force by impeller |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CNB200610038596XA CN100365289C (en) | 2006-03-03 | 2006-03-03 | Multi-stage centrifugal pump capable of self-balancing axial force by impeller |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN1815039A true CN1815039A (en) | 2006-08-09 |
| CN100365289C CN100365289C (en) | 2008-01-30 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CNB200610038596XA Expired - Fee Related CN100365289C (en) | 2006-03-03 | 2006-03-03 | Multi-stage centrifugal pump capable of self-balancing axial force by impeller |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN100365289C (en) |
Cited By (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102135100A (en) * | 2010-01-25 | 2011-07-27 | 格伦德福斯管理联合股份公司 | Centrifugal pump assembly |
| CN101936304B (en) * | 2010-01-04 | 2012-04-04 | 江苏大学 | Bearing insert to be inserted in inner hole part of plastic flow deflector shell of engineering plastic well pump |
| CN102878104A (en) * | 2012-10-25 | 2013-01-16 | 浙江佳力科技股份有限公司 | Axial force balanced structure of multilevel central opening type centrifugal pump |
| CN103062126A (en) * | 2012-06-28 | 2013-04-24 | 福建省银象电器有限公司 | Pump unit structure of submersible pump for high head well |
| WO2013131351A1 (en) * | 2012-03-09 | 2013-09-12 | 江苏大学 | Multi-stage submersible pump for mines |
| CN103573710A (en) * | 2013-11-07 | 2014-02-12 | 江苏大学 | Compact type reverse guide vane |
| CN112733351A (en) * | 2020-12-31 | 2021-04-30 | 沈阳透平机械股份有限公司 | Method and device for processing axial force data of centrifugal compressor impeller |
Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102678614A (en) * | 2012-04-06 | 2012-09-19 | 江苏大学 | Multistage centrifugal pump with completely balanced axial force of impeller |
Family Cites Families (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US3779668A (en) * | 1972-05-11 | 1973-12-18 | Mcneil Corp | Stage for a centrifugal pump |
| US4304104A (en) * | 1980-05-02 | 1981-12-08 | Northern Natural Gas Company | Pitot heat pump |
| CN1006321B (en) * | 1987-03-05 | 1990-01-03 | 江苏工学院 | Balance unit for pump axial force |
| DE4310466A1 (en) * | 1993-03-31 | 1994-10-06 | Klein Schanzlin & Becker Ag | Pump stage in sheet metal construction |
| JP3497962B2 (en) * | 1996-12-13 | 2004-02-16 | 株式会社 日立インダストリイズ | Centrifugal fluid machine |
| CN2444077Y (en) * | 2000-10-15 | 2001-08-22 | 山东双轮集团股份有限公司 | Axial balancing device for liquid pump |
| JP2003013883A (en) * | 2001-06-29 | 2003-01-15 | Nikkiso Co Ltd | Centrifugal pump |
| RU2260715C1 (en) * | 2004-02-09 | 2005-09-20 | ОАО "Омское машиностроительное конструкторское бюро" | Centrifugal gear pump |
-
2006
- 2006-03-03 CN CNB200610038596XA patent/CN100365289C/en not_active Expired - Fee Related
Cited By (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101936304B (en) * | 2010-01-04 | 2012-04-04 | 江苏大学 | Bearing insert to be inserted in inner hole part of plastic flow deflector shell of engineering plastic well pump |
| CN102135100A (en) * | 2010-01-25 | 2011-07-27 | 格伦德福斯管理联合股份公司 | Centrifugal pump assembly |
| CN102135100B (en) * | 2010-01-25 | 2014-10-29 | 格伦德福斯管理联合股份公司 | Centrifugal pump assembly |
| WO2013131351A1 (en) * | 2012-03-09 | 2013-09-12 | 江苏大学 | Multi-stage submersible pump for mines |
| CN103062126A (en) * | 2012-06-28 | 2013-04-24 | 福建省银象电器有限公司 | Pump unit structure of submersible pump for high head well |
| CN102878104A (en) * | 2012-10-25 | 2013-01-16 | 浙江佳力科技股份有限公司 | Axial force balanced structure of multilevel central opening type centrifugal pump |
| CN103573710A (en) * | 2013-11-07 | 2014-02-12 | 江苏大学 | Compact type reverse guide vane |
| CN112733351A (en) * | 2020-12-31 | 2021-04-30 | 沈阳透平机械股份有限公司 | Method and device for processing axial force data of centrifugal compressor impeller |
| CN112733351B (en) * | 2020-12-31 | 2024-03-01 | 沈阳透平机械股份有限公司 | Method and device for processing axial force data of impeller of centrifugal compressor |
Also Published As
| Publication number | Publication date |
|---|---|
| CN100365289C (en) | 2008-01-30 |
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| C06 | Publication | ||
| PB01 | Publication | ||
| C10 | Entry into substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| EE01 | Entry into force of recordation of patent licensing contract |
Assignee: Taizhou Jiadi Pump Industry Co., Ltd. Assignor: Jiangsu University Contract fulfillment period: 2008.7.8 to 2018.7.7 Contract record no.: 2009330001086 Denomination of invention: Multi-stage centrifugal pump capable of self-balancing axial force by impeller Granted publication date: 20080130 License type: Exclusive license Record date: 2009.5.20 |
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| LIC | Patent licence contract for exploitation submitted for record |
Free format text: EXCLUSIVE LICENSE; TIME LIMIT OF IMPLEMENTING CONTACT: 2008.7.8 TO 2018.7.7; CHANGE OF CONTRACT Name of requester: TAIZHOU JIADI PUMP INDUSTRY CO., LTD. Effective date: 20090520 |
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| EC01 | Cancellation of recordation of patent licensing contract |
Assignee: Taizhou Jiadi Pump Industry Co., Ltd. Assignor: Jiangsu University Contract record no.: 2009330001086 Date of cancellation: 20100820 |
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| EE01 | Entry into force of recordation of patent licensing contract |
Assignee: Jiangsu Yatai Pump Co., Ltd. Assignor: Jiangsu University Contract record no.: 2011320000311 Denomination of invention: Multi-stage centrifugal pump capable of self-balancing axial force by impeller Granted publication date: 20080130 License type: Exclusive License Open date: 20060809 Record date: 20110317 |
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| EC01 | Cancellation of recordation of patent licensing contract |
Assignee: Jiangsu Yatai Pump Co., Ltd. Assignor: Jiangsu University Contract record no.: 2011320000311 Date of cancellation: 20130326 |
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| LICC | Enforcement, change and cancellation of record of contracts on the licence for exploitation of a patent or utility model | ||
| EE01 | Entry into force of recordation of patent licensing contract |
Application publication date: 20060809 Assignee: JIANGSU FEIYUE PUMP GROUP CO., LTD. Assignor: Jiangsu University Contract record no.: 2016320000039 Denomination of invention: Multi-stage centrifugal pump capable of self-balancing axial force by impeller Granted publication date: 20080130 License type: Exclusive License Record date: 20160229 |
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| LICC | Enforcement, change and cancellation of record of contracts on the licence for exploitation of a patent or utility model | ||
| EC01 | Cancellation of recordation of patent licensing contract | ||
| EC01 | Cancellation of recordation of patent licensing contract |
Assignee: JIANGSU FEIYUE PUMP GROUP CO., LTD. Assignor: Jiangsu University Contract record no.: 2016320000039 Date of cancellation: 20171206 |
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| CF01 | Termination of patent right due to non-payment of annual fee | ||
| CF01 | Termination of patent right due to non-payment of annual fee |
Granted publication date: 20080130 Termination date: 20180303 |