CN87100241A - Balance unit for pump axial force - Google Patents
Balance unit for pump axial force Download PDFInfo
- Publication number
- CN87100241A CN87100241A CN87100241.8A CN87100241A CN87100241A CN 87100241 A CN87100241 A CN 87100241A CN 87100241 A CN87100241 A CN 87100241A CN 87100241 A CN87100241 A CN 87100241A
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- China
- Prior art keywords
- pump
- axial force
- impeller
- balance unit
- low pressure
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- Control Of Non-Positive-Displacement Pumps (AREA)
Abstract
A kind of pump that is used for is especially for the balance unit for pump axial force of deep well submerged pump, oil-immersed pump and sectional type multistage pump.The present invention is after the not level impeller of pump, a pair of mechanical seal end surface friction pair is housed, the end-face friction pair separates liquid and the atmosphere (or low pressure area) of impeller outlet, utilizes the poor of the low pressure that acts on preceding pressure of impeller and back, and balanced action automatically is in epitrochanterian axial force.Characteristics such as device of the present invention has simple in structure, and leakage rate is little, and sand controlling result is good, and reliability and the working life that can improve unit.
Description
The present invention relates to a kind of pump that is used for, especially for the balance unit for pump axial force of deep well submerged pump, oil-immersed pump and sectional type multistage pump.
Pump is on-stream, and effect has axial force on axle usually, and this power will spur rotor axial and move.Therefore, must manage balance or eliminate this axial force, just can make the pump proper functioning.Traditional Equilibrator is a lot, as related equalizing orifice Equilibrator of balance muscle, balancing drum, Balance disc and U.S. Pat 4086020 etc.These balance methods can play the effect of ballast pump axial force, but also exist leakage rate big, shortcomings such as complex structure, and dustproof effect is poor when being used for the impure liquid of pump.For example, deep well submerged pump is owing to be subjected to the restriction of hole diameter, the bearing capacity of thrust-bearing is limited, therefore axial force balance is the key issue of high-lift submersible pump or oil-immersed pump always, traditional various balancing axial power apparatus, though energy balancing axial thrust, but not structure very complicated (as symmetric arrangement), be exactly that leakage rate is very big, the efficient of pump obviously descended, in addition, present submersible pump mostly is contained in thrust-bearing the bottom of pump below motor, under the effect of axial force of impeller at different levels, transmission shaft is in operation under the depression bar state, the serious wear that choma etc. are located like this.The life-span of general high lift mining diving pump is about 1 year, the life-span Only Six Months of bore-hole immersed pump.
Balance unit for pump axial force of the present invention has been broken the working principle and the structural type of conventional balanced device, is a pair of mechanical seal end surface friction pair is loaded on not after the level impeller, utilizes mechanical sealing technology to come balancing axial thrust.End-face friction is secondary to separate not liquid and the atmosphere (or low pressure area) of level impeller outlet, utilizes the poor of the low pressure that acts on preceding pressure of grade impeller not and back, and balanced action automatically is in epitrochanterian axial force.Though the not stage pressure of pump is higher, adopt balanced mechanical seal end-face friction pair, can control face pressure artificially, so frictional power loss is little, have long working life.
Balance unit for pump axial force of the present invention according to the specific performance and the dimensional parameters of pump, by force analysis, calculates the physical dimension of end-face friction pair.Calculating shows that the secondary external diameter of end-face friction is 0.8～1.0 times of pump impeller choma diameter, pressure height when pump, size hour, can make low-pressure cavity pass to a certain intergrade, increase the secondary external diameter of end-face friction simultaneously, otherwise, when the size of pump very big, when the relative velocity of end-face friction pair is very high, can reduce the secondary external diameter of end-face friction, but can only the balance portion axial force.Therefore the degree of balancing axial thrust can be grasped flexibly.
Balance unit for pump axial force of the present invention is compared with traditional Equilibrator and is had the following advantages:
1, form high and low pressure reduction balancing axial thrust by sealing, does not almost have leakage, the leakage rate of conventional balanced device is reclaimed, so adopts this device, the energy-saving effect average out to 4% to 10% of pump;
2, simple and reliable for structure, even the secondary wearing and tearing of end-face friction, just leaking increases, and axial force still can obtain balance;
3, because very few by the leakage of end-face friction pair, the liquid before the end-face friction pair almost is in no flowing state, utilizes simple sand control installation, can obtain good sand controlling result, thereby this device also is applicable to impure liquid pump.
Description of drawings:
Accompanying drawing 1: deep well submerged pump axial thrust balancing devices sketch
Embodiment:
On deep well submerged pump, use the present invention's (seeing accompanying drawing).At not back dress rotating ring (2), the stationary ring (1) of level impeller (3), constitute a pair of end face friction pair, be grade impeller (3) outlet pressure not before the end-face friction pair, thereafter by return port (5) communicate with well chamber or a certain low pressure stage (shown in the arrow among the figure).Level impeller (3) inlet pressure and impeller back low pressure is not poor, forms the equilibrant that points to the impeller rear, balanced action on impellers at different levels, point to the importer to axial force.On deep well submerged pump, use the present invention, except that having aforementioned advantages, also can make the stressed of transmission shaft become tension, thereby improve the stress of rotor, can improve greatly unit operation reliability and life-span from pressurized.
Claims (3)
1, a kind of balance unit for pump axial force.It is characterized in that Equilibrator by be contained in pump not level impeller [3] afterwards, the mechanical seal end surface friction pair composition that the fluid of not level impeller [3] outlet and atmosphere (or low pressure area) are separated.
2, balance unit for pump axial force according to claim 1 is characterized in that the end-face friction minor flank has the return port (5) that communicates with well chamber or a certain low pressure stage.
3, balance unit for pump axial force according to claim 1, the outside dimension that it is characterized in that the end-face friction pair are 0.8～1.0 times choma diameter.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 87100241 CN1006321B (en) | 1987-03-05 | 1987-03-05 | Balance unit for pump axial force |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 87100241 CN1006321B (en) | 1987-03-05 | 1987-03-05 | Balance unit for pump axial force |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN87100241A true CN87100241A (en) | 1988-09-14 |
| CN1006321B CN1006321B (en) | 1990-01-03 |
Family
ID=4812782
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN 87100241 Expired CN1006321B (en) | 1987-03-05 | 1987-03-05 | Balance unit for pump axial force |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN1006321B (en) |
Cited By (12)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN1082151C (en) * | 1998-12-22 | 2002-04-03 | 王宝利 | Self-balanced thrust blade wheel for centrifugal pump |
| CN100365289C (en) * | 2006-03-03 | 2008-01-30 | 江苏大学 | Multi-stage centrifugal pump capable of self-balancing axial force by impeller |
| CN101896723B (en) * | 2007-12-17 | 2013-05-01 | 罗伯特·博世有限公司 | Liquid pump |
| CN105736479A (en) * | 2016-04-05 | 2016-07-06 | 江苏振华泵业制造有限公司 | Pressure self-balance device for inlet of centrifugal pump |
| CN105745452A (en) * | 2013-11-21 | 2016-07-06 | Ksb 股份公司 | Load-relieving device |
| CN105736445A (en) * | 2016-04-05 | 2016-07-06 | 江苏振华泵业制造有限公司 | Horizontal centrifugal pump with built-in axial force balancing device |
| CN106151095A (en) * | 2016-08-31 | 2016-11-23 | 天津甘泉集团有限公司 | A kind of axial force balancing device for electric diving pump |
| CN108730226A (en) * | 2017-04-25 | 2018-11-02 | 西安航空学院 | A kind of peripheral pump with floating side plate |
| CN109424578A (en) * | 2017-08-23 | 2019-03-05 | 苏尔寿管理有限公司 | Bearing device with lifting device |
| CN110869616A (en) * | 2017-05-10 | 2020-03-06 | Itt制造企业有限责任公司 | Multi-stage pump with enhanced thrust balancing features |
| CN114278605A (en) * | 2021-12-13 | 2022-04-05 | 扬州大学 | Hub friction pair of vertical centrifugal pump with floating impeller |
| CN115324911A (en) * | 2022-10-12 | 2022-11-11 | 中国核动力研究设计院 | Supercritical carbon dioxide compressor and coaxial power generation system |
-
1987
- 1987-03-05 CN CN 87100241 patent/CN1006321B/en not_active Expired
Cited By (16)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN1082151C (en) * | 1998-12-22 | 2002-04-03 | 王宝利 | Self-balanced thrust blade wheel for centrifugal pump |
| CN100365289C (en) * | 2006-03-03 | 2008-01-30 | 江苏大学 | Multi-stage centrifugal pump capable of self-balancing axial force by impeller |
| CN101896723B (en) * | 2007-12-17 | 2013-05-01 | 罗伯特·博世有限公司 | Liquid pump |
| US10094388B2 (en) | 2013-11-21 | 2018-10-09 | Ksb Aktiengesellschaft | Load-relieving device |
| CN105745452A (en) * | 2013-11-21 | 2016-07-06 | Ksb 股份公司 | Load-relieving device |
| JP2016540152A (en) * | 2013-11-21 | 2016-12-22 | カーエスベー・アクチエンゲゼルシャフトＫｓｂ Ａｋｔｉｅｎｇｅｓｅｌｌｓｃｈａｆｔ | Load relief device |
| CN105736445A (en) * | 2016-04-05 | 2016-07-06 | 江苏振华泵业制造有限公司 | Horizontal centrifugal pump with built-in axial force balancing device |
| CN105736479A (en) * | 2016-04-05 | 2016-07-06 | 江苏振华泵业制造有限公司 | Pressure self-balance device for inlet of centrifugal pump |
| CN106151095A (en) * | 2016-08-31 | 2016-11-23 | 天津甘泉集团有限公司 | A kind of axial force balancing device for electric diving pump |
| CN108730226A (en) * | 2017-04-25 | 2018-11-02 | 西安航空学院 | A kind of peripheral pump with floating side plate |
| CN108730226B (en) * | 2017-04-25 | 2020-05-19 | 西安航空学院 | Peripheral pump with floating side plate |
| CN110869616A (en) * | 2017-05-10 | 2020-03-06 | Itt制造企业有限责任公司 | Multi-stage pump with enhanced thrust balancing features |
| CN109424578A (en) * | 2017-08-23 | 2019-03-05 | 苏尔寿管理有限公司 | Bearing device with lifting device |
| CN114278605A (en) * | 2021-12-13 | 2022-04-05 | 扬州大学 | Hub friction pair of vertical centrifugal pump with floating impeller |
| CN115324911A (en) * | 2022-10-12 | 2022-11-11 | 中国核动力研究设计院 | Supercritical carbon dioxide compressor and coaxial power generation system |
| CN115324911B (en) * | 2022-10-12 | 2023-08-22 | 中国核动力研究设计院 | Supercritical carbon dioxide compressor and coaxial power generation system |
Also Published As
| Publication number | Publication date |
|---|---|
| CN1006321B (en) | 1990-01-03 |
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| C06 | Publication | ||
| PB01 | Publication | ||
| C10 | Entry into substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| C13 | Decision | ||
| C14 | Grant of patent or utility model | ||
| C19 | Lapse of patent right due to non-payment of the annual fee |