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 PDF

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Publication number
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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China
Prior art keywords
impeller
axial force
centrifugal pump
front shroud
face seal
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CN 200610038596
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Chinese (zh)
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CN100365289C (en
Inventor
陆伟刚
施卫东
张启华
张金风
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Jiangsu University
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Jiangsu University
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Publication of CN100365289C publication Critical patent/CN100365289C/en
Expired - Fee Related legal-status Critical Current
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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

The multistage centrifugal pump of a kind of impeller self balancing axial thrust
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.
CNB200610038596XA 2006-03-03 2006-03-03 Multi-stage centrifugal pump capable of self-balancing axial force by impeller Expired - Fee Related CN100365289C (en)

Priority Applications (1)

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CNB200610038596XA CN100365289C (en) 2006-03-03 2006-03-03 Multi-stage centrifugal pump capable of self-balancing axial force by impeller

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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

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CN1815039A true CN1815039A (en) 2006-08-09
CN100365289C CN100365289C (en) 2008-01-30

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Cited By (6)

* Cited by examiner, † Cited by third party
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

Families Citing this family (1)

* Cited by examiner, † Cited by third party
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

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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

Cited By (7)

* Cited by examiner, † Cited by third party
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

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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

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Free format text: EXCLUSIVE LICENSE; TIME LIMIT OF IMPLEMENTING CONTACT: 2008.7.8 TO 2018.7.7; CHANGE OF CONTRACT

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Denomination of invention: Multi-stage centrifugal pump capable of self-balancing axial force by impeller

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