CN101666330A - Method and structure for eliminating axial force of impeller of canned motor pump - Google Patents
Method and structure for eliminating axial force of impeller of canned motor pump Download PDFInfo
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- CN101666330A CN101666330A CN200810213430A CN200810213430A CN101666330A CN 101666330 A CN101666330 A CN 101666330A CN 200810213430 A CN200810213430 A CN 200810213430A CN 200810213430 A CN200810213430 A CN 200810213430A CN 101666330 A CN101666330 A CN 101666330A
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- impeller
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- pump housing
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Abstract
The invention discloses a balance structure for eliminating the axial force of an impeller of a canned motor pump. The improved balance structure for the axial force of the canned motor pump consistsof a pump body, a pump shaft, the impeller and a bearing seat, wherein the bearing seat is arranged in the pump body; the impeller is sleeved on the pump spindle and positioned in front of the bearingseat. By using a variable gap arranged axially, a balance hole of the impeller arranged fixedly and a first pressure cavity and a second pressure cavity communicated with each other through the balance hole to form a hydraulic dynamic balance system, the balance structure can effectively balance the axial force in real time, reduce the use of a wearing part thrust bearing, reduce bearing friction, also reduce the failure rate of a pump, and improve the service life of the pump and the efficiency of the pump.
Description
Affiliated technical field
The present invention relates to the axial force balance technology in pump technology field, particularly canned motorpump.
Background technique
In the prior art, canned motorpump does not have gland seal device, and motor and pump are coaxial, utilizes housing that stator, rotor and fed sheet of a media are separated, and self fed sheet of a media is adopted in motor cooling and bearing lubrication, and axle supports and adopts sliding bearing.Canned motorpump is on-stream, will produce axial force when front shroud of impeller, back shroud pressure imbalance, and this axial force acts on the thrust-bearing by rotor assembly.Existing pump shaft has equalizing orifice mode and back blade mode to the equilibrium of forces technology.But prior art can not the complete equilibrium axial force, and remaining axial force causes bigger end thrust backward.Therefore existing canned motorpump all can not be avoided contacting between the thrust face of thrust disc and thrust-bearing effectively, and this can cause the wearing and tearing of thrust-bearing.Simultaneously, in actual use, the proportion of fed sheet of a media, viscosity all exert an influence to the size and Orientation of axial force, and the change of flow also can cause axial force to change, so prior art can not adapt to the axial force of fluctuation automatically.In order to address the above problem, number of patent application is: 200410084383.1, publication number is: the disclosure of the Invention of CN1779275A a kind of method of axial force balance, the structure of this method is by the pump housing, pump shaft, impeller and bearing support constitute, described bearing support is arranged in the described pump housing, described bearing is arranged in the described bearing support, described impeller set is located on the described pump shaft and is positioned at the place ahead of described bearing support, wherein, the front shroud of described impeller is provided with a cylindrical boss, the shaft axis of described cylindrical boss overlaps with the shaft axis of described pump shaft, the pump housing inboard of described impeller front side is provided with one first cylindrical cavity, the shaft axis of described first cylindrical cavity overlaps with the shaft axis of described cylindrical boss, described cylindrical boss is arranged in described first cylindrical cavity, be provided with first gap between the periphery of inner wall face of the outer peripheral surface of described cylindrical boss and described first cylindrical cavity, the back shroud of described impeller is provided with the cylindric bulge loop of a projection, the shaft axis of described cylindric bulge loop overlaps with the shaft axis of described pump shaft, the pump housing inboard of described impeller rear side is provided with one second cylindrical cavity, the shaft axis of described second cylindrical cavity overlaps with the shaft axis of described cylindric bulge loop, described cylindric bulge loop is arranged in second cylindrical cavity, be provided with second gap between the periphery of inner wall face of the outer circumferential surface of described cylindric bulge loop and described second cylindrical cavity, end face direction to the back shroud of described impeller on the described bearing support is provided with a bump, is provided with a third space between the end face of the end face of described bump and the back shroud of described impeller.The working principle of this invention is: when axial force increased forward, impeller moved forward, and axially the third space that is provided with increases, leakage rate increases, the pressure of back shroud of impeller descends, and under the effect of front shroud of impeller pressure, impeller then moves backward, axially the third space that is provided with reduces, leakage rate reduces, and the pressure of back shroud of impeller increases, under the effect of back shroud of impeller pressure, impeller then moves forward, and above process makes impeller reach transient equiliblium.
In the above working principle, show according to experiment, " when axial force increases forward; impeller moves forward; axially the third space that is provided with increases; leakage rate increases; the pressure of back shroud of impeller descends; under the effect of front shroud of impeller pressure, impeller then moves backward ", the reason that impeller moves backward is not because of " third space increases, the leakage rate increase "; because when the third space increase; when leakage rate increased, third space had lost effect, at this moment the mobile backward influencing factor of impeller is: certain gap (this gap does not have specific pointing out in its structure and principle) on the front shroud of impeller between inboard first cylindrical cavity of the pump housing of cylindrical boss and impeller front side; be that this gap reduces; leakage rate reduces, the low pressure in first cylindrical cavity shifts to second cylindrical cavity by equalizing orifice, makes second cylindrical cavity be in low-pressure state; under the action of pressure of impeller front and back, make impeller move backward; The argumentation of " impeller then moves backward; axially the third space that is provided with reduces; leakage rate reduces; the pressure of back shroud of impeller increases; under the effect of back shroud of impeller pressure; impeller then moves forward " also lacks condition, though third space at this moment is to play a crucial role, but principle then is: impeller moves backward, axially the third space that is provided with reduces, and leakage rate reduces, and the low pressure in second cylindrical cavity shifts to first cylindrical cavity by equalizing orifice, under the action of pressure, impeller then moves forward before and after impeller.
In its principle, do not mention the existence of the impeller balance hole between first cylindrical cavity and second cylindrical cavity, more do not explain equalizing orifice effect therein, if its structure does not have equalizing orifice, the transient equiliblium of impeller just can't realize in this structure at all so.
In its structure, the existence in described first gap and second gap does not have practical significance to the proportion viscosity of fed sheet of a media and the variation of flow size, because the decision fed sheet of a media passes through, should be certain gap between inboard first cylindrical cavity of the pump housing of cylindrical boss and impeller front side on the front shroud of third space, impeller, be the passing capacity that the clearance limit that occurs in the dynamic process in these two gaps has determined fed sheet of a media.
Above working principle does not find that impeller can reach the principle essence of transient equiliblium, above structure (supposing has under the prerequisite of equalizing orifice at impeller) also just makes impeller reach special case of transient equiliblium, and in this special case complex structure, dynamic clearance be provided with fuzzy and unreasonable.The result who causes like this is: can not go to make various useful scientific and reasonable structures according to correct essential principle, make impeller can indiscriminately ad. as one wishes reach transient equiliblium under different operating modes.Also make the decrease in efficiency of pump.
Summary of the invention
The problems of the prior art to be solved by this invention are: discovery can make the principle essence of impeller shaft to transient equiliblium, can make the structure of different impeller shafts according to principle design, make impeller can really accomplish to be issued to transient equiliblium at different pump body structures and working condition to transient equiliblium.
The present invention solves the aforementioned problems in the prior the technological scheme that is adopted to be: described this improved axial force balancing structure of shielded pump is made of the pump housing, pump shaft, impeller and bearing support, described bearing support is arranged in the described pump housing, described impeller set is located on the described pump shaft and is positioned at the place ahead of described bearing support, wherein, the shaft axis of the front-end face of the described pump housing and front shroud of impeller end face and the shaft axis of described pump shaft are returned, and form dynamic first gap between the front-end face of the pump housing and the front shroud of impeller end face.The bearing support front-end face of the described pump housing and the shaft axis of back shroud of impeller end face and the shaft axis of described pump shaft are returned, and form dynamic second gap between bearing support front-end face and the back shroud of impeller end face.Form first pressure space between described impeller and the water intake, form second pressure space between described impeller and the bearing support front-end face.Communicate by the equalizing orifice that is located on the impeller between first pressure space and second pressure space.
Further, the front-end face of the described pump housing is parallel with the front shroud of impeller end face on the same shaft axis, and the bearing support front-end face of the described pump housing is parallel with the back shroud of impeller end face on the same shaft axis.
Further again, between described first, second gap, can be at the position of impeller towards the front-end face and the bearing support end face of the pump housing, two annular protrusion branches are set, the end face of annular protrusion is parallel with the bearing support end face with the front-end face of the pump housing, and the big I of the end face of annular protrusion requires to be provided with according to reality.Also can be at the front-end face of the pump housing and bearing support end face position towards impeller, two annular protrusion branches are set, the end face of two annular protrusions is parallel with the back shroud of impeller end face with the front shroud of impeller end face respectively, and the big I of the end face of annular protrusion requires to be provided with according to reality.
Further again, the impeller balance hole of described UNICOM first pressure space and second pressure space has two or more at least, and is evenly distributed between each equalizing orifice.
Further again, the present principles structure can be used in the multistage pump too, and stack gets final product to the booster cavity of this structure.
Further again, described impeller can be on described pump shaft and endwisely slips.
Working principle of the present invention is: when being low pressure in first pressure space, the first pressure space internal pressure is less than the pressure of second pressure space, and under the action of pressure, impeller moves toward first pressure space before and after impeller.First gap that axially be provided with this moment reduces, leakage rate reduces, when first gap further reduces, when leakage rate further reduces, low pressure in first pressure space shifts to second pressure space by the equalizing orifice on the impeller, when the second pressure space internal pressure during less than the pressure of first pressure space, under the action of pressure, impeller moves to second pressure space before and after impeller.When impeller further moves toward second pressure space, this moment, second gap reduced, leakage rate reduces, low pressure area shifts to first pressure space by equalizing orifice again, under the action of pressure of impeller front and back, impeller stops to move and moving to first pressure space to second pressure space, makes impeller search out an equilibrium position automatically in the above process, reaches the purpose of impeller transient equiliblium.
The magnitude relationship of equalizing orifice is to the limit in gap size and pump efficiency and medium passing capacity, and promptly equalizing orifice is big more, and the clearance limit in the one the second gaps is also big more, and pump efficiency is more little, and the ability of conveying different specific weight viscosity medium is strong more.Equalizing orifice is more little, and the clearance limit in the one the second gaps is also more little, and pump efficiency is high more, carries the ability of different specific weight viscosity medium weak more.This can be according to being provided with flexibly under the different service conditions.Because first gap and second gap are very little, can improve the efficient of pump greatly.
The present invention and prior art contrast, its effect are actively with tangible.The present invention utilizes the variable gap of axial setting, the impeller balance hole that fixedly installs, the one the second pressure spaces by the equalizing orifice intercommunication to constitute the hydraulic pressure homestat, can be effectively balancing axial thrust in real time, reduce the use of easily damaged parts thrust-bearing, reduce pivot friction, further reduce the rate of fault of pump, improved the pump life-span; Utilize the relation of equalizing orifice size and clearance limit, can adjust the peak efficiency of pump, can remedy the loss in efficiency of canned motorpump, can improve the efficient of canned motorpump greatly because of using impeller balance hole to leak; Because the one the second gaps can be done very for a short time, pump efficiency further improves, and has surpassed the efficient of conventional water pump; The volume and weight of pump has also correspondingly reduced.
Description of drawings
Fig. 1 is the structural representation of improved axial force balancing structure of shielded pump of the present invention.The pump housing 1, impeller 2, pump shaft 3, bearing 4, bearing support 5, first pressure space 6, second pressure space 7, impeller balance hole 8, first dynamic clearance 9, second dynamic clearance 10, back shroud of impeller end face annular projection 11, front shroud of impeller end face annular projection 12, pump housing front-end face annular protrusion divide 13, bearing support end face annular projection 14.
Embodiment:
As shown in Figure 1, improved canned motorpump equilibrium structure of the present invention is by the pump housing 1, pump shaft 3, impeller 2, bearing support 5 constitutes, described bearing support 5 is arranged in the described pump housing 1, be provided with bearing 4 in the described bearing support 5, described pump shaft 3 is arranged in the bearing 4, described impeller 2 is set on the described pump shaft 3 and is positioned at the place ahead of described bearing support 5, wherein, described impeller 2, pump housing front-end face, bearing support 5 front-end faces overlap with the shaft axis of pump shaft 3, described first pressure space 6 and second pressure space 7 communicate by impeller balance hole 8, described pump housing front-end face and impeller 2 front shroud end faces form first dynamic clearance 9, and described bearing support 5 front-end faces and impeller 2 back shroud end faces form second dynamic clearance 10.
In a preferred embodiment of the invention, described pump housing front-end face is parallel with impeller 2 front shroud end faces, and described bearing support 5 front-end faces are parallel with impeller 2 back shroud end faces.
In a preferred embodiment of the invention, at described impeller respectively towards the position of the front-end face and the bearing support end face of the pump housing, two annular protrusion branches are set, be back shroud of impeller end face annular projection 11 and front shroud of impeller end face annular projection 12, the end face of annular protrusion is parallel with the bearing support end face with the front-end face of the pump housing.
In a preferred embodiment of the invention, at the front-end face of the described pump housing and bearing support end face position towards impeller, two annular protrusion branches are set, be pump housing front-end face annular protrusion divide 13 and the end face of 14, two annular protrusions of bearing support end face annular projection parallel with the front shroud of impeller end face respectively with the back shroud of impeller end face.
In a preferred embodiment of the invention, impeller 2 is set on the pump shaft 3 and can be free to slide along pump shaft.
Claims (5)
1. improved axial force balancing structure of shielded pump, by the pump housing, pump shaft, impeller and bearing support constitute, described bearing support is arranged in the described pump housing, described impeller set is located on the described pump shaft and is positioned at the place ahead of described bearing support, it is characterized in that: the shaft axis of the front-end face of the described pump housing and front shroud of impeller end face overlaps with the shaft axis of described pump shaft, form dynamic first gap between the front-end face of the pump housing and the front shroud of impeller end face, the bearing support front-end face of the described pump housing and the shaft axis of back shroud of impeller end face overlap with the shaft axis of described pump shaft, form dynamic second gap between bearing support front-end face and the back shroud of impeller end face, form first pressure space between described impeller and the water intake, form second pressure space between described impeller and the bearing support, communicate by the equalizing orifice that is located on the impeller between first pressure space and second pressure space.
2. improved according to claim 1 axial force balancing structure of shielded pump, it is characterized in that: the front-end face of the described pump housing is parallel with the front shroud of impeller end face on the same shaft axis, and the bearing support front-end face of the described pump housing is parallel with the back shroud of impeller end face on the same shaft axis.
3. improved according to claim 1 axial force balancing structure of shielded pump, it is characterized in that: described first, between second gap, can be at the position of impeller towards the front-end face and the bearing support end face of the pump housing, two annular protrusion branches are set, the end face of annular protrusion is parallel with the bearing support end face with the front-end face of the pump housing, the big I of the end face of annular protrusion requires to be provided with according to reality, also can be at the front-end face of the pump housing and bearing support end face position towards impeller, two annular protrusion branches are set, the end face of two annular protrusions is parallel with the back shroud of impeller end face with the front shroud of impeller end face respectively, and the big I of the end face of annular protrusion requires to be provided with according to reality.
4. improved according to claim 1 axial force balancing structure of shielded pump is characterized in that: the impeller balance hole of described UNICOM first pressure space and second pressure space has two or more at least, and is evenly distributed between each equalizing orifice.
5. improved according to claim 1 axial force balancing structure of shielded pump is characterized in that: described impeller can be on described pump shaft and endwisely slips.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN200810213430A CN101666330A (en) | 2008-09-02 | 2008-09-02 | Method and structure for eliminating axial force of impeller of canned motor pump |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN200810213430A CN101666330A (en) | 2008-09-02 | 2008-09-02 | Method and structure for eliminating axial force of impeller of canned motor pump |
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| Publication Number | Publication Date |
|---|---|
| CN101666330A true CN101666330A (en) | 2010-03-10 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN200810213430A Pending CN101666330A (en) | 2008-09-02 | 2008-09-02 | Method and structure for eliminating axial force of impeller of canned motor pump |
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Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN108105142A (en) * | 2017-12-27 | 2018-06-01 | 合肥新沪屏蔽泵有限公司 | A kind of big flow low lift shielding force at direction of pump spindle adjusting apparatus |
-
2008
- 2008-09-02 CN CN200810213430A patent/CN101666330A/en active Pending
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN108105142A (en) * | 2017-12-27 | 2018-06-01 | 合肥新沪屏蔽泵有限公司 | A kind of big flow low lift shielding force at direction of pump spindle adjusting apparatus |
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Addressee: Lian Ronghui Document name: Notification of before Expiration of Request of Examination as to Substance |
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Open date: 20100310 |