CN102392832A - Full-lift centrifugal pump - Google Patents

Full-lift centrifugal pump Download PDF

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Publication number
CN102392832A
CN102392832A CN2011103063992A CN201110306399A CN102392832A CN 102392832 A CN102392832 A CN 102392832A CN 2011103063992 A CN2011103063992 A CN 2011103063992A CN 201110306399 A CN201110306399 A CN 201110306399A CN 102392832 A CN102392832 A CN 102392832A
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CN
China
Prior art keywords
guide vane
impeller
centrifugal pump
lift
flow
Prior art date
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.)
Pending
Application number
CN2011103063992A
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Chinese (zh)
Inventor
陆伟刚
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Jiangsu University
Original Assignee
Jiangsu University
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Jiangsu University filed Critical Jiangsu University
Priority to CN2011103063992A priority Critical patent/CN102392832A/en
Publication of CN102392832A publication Critical patent/CN102392832A/en
Priority to PCT/CN2012/079141 priority patent/WO2013044675A1/en
Pending legal-status Critical Current

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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
    • F04D1/00—Radial-flow pumps, e.g. centrifugal pumps; Helico-centrifugal pumps
    • F04D1/06—Multi-stage pumps
    • F04D1/063—Multi-stage pumps of the vertically split casing type
    • 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
    • F04D29/4273—Casings; Connections of working fluid for radial or helico-centrifugal pumps especially adapted for liquid pumps suction eyes
    • 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
    • F04D29/44—Fluid-guiding means, e.g. diffusers
    • F04D29/445—Fluid-guiding means, e.g. diffusers especially adapted for liquid pumps
    • F04D29/448—Fluid-guiding means, e.g. diffusers especially adapted for liquid pumps bladed diffusers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
    • F05D2250/00—Geometry
    • F05D2250/70—Shape

Abstract

The invention relates to a full-lift centrifugal pump, which comprises one pair or multiple pairs of impellers and a flow-guiding shell which are in serial connection, wherein the impellers are centrifugal impellers; an inverted guide vane blade is arranged in the flow-guiding shell; pumped water enters into an impeller inlet by the inverted guide vane blade; an outlet mounting angle of the inverted guide vane blade is less than 50 degrees; and for a first-stage impeller of a multi-stage centrifugal pump and the impeller of a single-stage centrifugal pump, an inlet guide vane is mounted in front of the impeller inlet and an outlet mounting angle of an inlet guide vane blade is less than 50 degrees. The multi-stage centrifugal pump with low specific speed and the single-stage centrifugal pump low with low specific speed manufactured according to the invention are both characterized by full lift, not only can be used efficiently and reliably under a high-lift and small-flow working condition but also can be safely used in an overload-free manner under a low-lift and high-flow working condition. The low-specific-speed impellers of the full-lift centrifugal pump can be more easily cast and the efficiency of the water pump is higher.

Description

A kind of total head centrifugal pump
Affiliated technical field
The present invention is that a kind of low specific speed does not have the overload centrifugal pump, especially should under high-lift low flow rate condition, use the total head centrifugal pump that also will under the low lift and large flow rate operating mode, use.
Background technique
At present; Known low specific speed centrifugal pump exists pump shaft power to reduce the rule that increases with lift mostly; When the power of necessary electromotor is not too big; Low specific speed centrifugal pump can only safe operation under high-lift operating mode, if under the low lift operating mode, use, and will the power overload and burn out motor.But a lot of low specific speed centrifugal pump, especially submersible pumps generally all can move the place to use, and use today under high-lift low flow rate condition, and possibly use under the low lift and large flow rate operating mode tomorrow, and this will take place that power overloads and the accident that burns out motor.Perhaps force us adopt the method for low load with strong power, supporting high power motor has strengthened investment so again, has wasted the energy.
For this reason; No. 89212885.2 patents of the patented technology that has earlier " the involute impeller that is used for rotary type fluid machine ", No. 90214606.8 patents " a kind of nothing overload low specific speed centrifugal pump impeller " and ZL200410014937.0 patent of invention " a kind of low specific speed centrifugal pump impeller design method " etc.; Improve the Changing Pattern of low specific speed centrifugal pump air horsepower through changing the impeller design method; Though obtained obvious effects but still had two problems: 1. too greatly perhaps the runner gap is too little for the cornerite of impeller blade, has increased difficulty to casting technique; 2. when improving low specific speed centrifugal pump air horsepower Changing Pattern,, pump efficiency is difficult to be up to state standards the energy-saving index of regulation to such an extent as to decreasing.
Summary of the invention
In order to overcome the deficiency that existing low specific speed centrifugal pump can not use under whole lift operating modes of water pump; The present invention provides a kind of total head centrifugal pump; Make the low specific speed centrifugal pump can safe operation under high-lift low flow rate condition; Can under the low lift and large flow rate operating mode, reliably use again, and the impeller manufacturing is easier, pump efficiency is also higher.
Technological scheme of the present invention is:
1. total head centrifugal pump of the present invention; Be composed in series by one or more pairs of impellers and blower inlet casing; Its impeller is a receded disk impeller; Its blower inlet casing contains the return guide vane blade, and the current of pumping get into impeller inlet through the return guide vane blade, and its main innovation is: the outlet laying angle of return guide vane blade is less than 50 degree.
The outlet laying angle of return guide vane blade is meant the sensing of return guide vane blade exit and the angle of impeller sense of rotation.The outlet laying angle of return guide vane blade is main creation of the present invention less than 50 degree.The outlet laying angle of the various return guide vane blades of existing multistage centrifugal pump is all greater than 55 degree; This is because the effect that existing multistage centrifugal pump is provided with return guide vane is exactly to change the circumferential speed component of velocity vector into the axis plane velocity component; Therefore the outlet laying angle of return guide vane blade is generally got about 80 degree, and minimum can be less than 55 degree yet.
The little exit angle return guide vane of the invention makes the velocity vector that gets into impeller inlet have bigger circumferential speed component, and this can reduce the original lift of impeller.But the size of circumferential speed component is directly proportional with the flow size, and therefore the declared working condition at low specific speed centrifugal pump is a low flow rate condition, and its circumferential speed component is very little, and lift reduces also seldom.And big flow operating mode, its circumferential speed component can be very big, so the lift reduction is also very big, and this just can reduce the water-horse power of big flow operating mode greatly, thereby makes low specific speed centrifugal pump at big flow operating mode non-overloading.
Because getting into the velocity vector of impeller inlet, the present invention has bigger circumferential speed component; And the sense of rotation of flow is identical with the sense of rotation of impeller; The flow angle of impeller inlet is just bigger, and therefore impeller inlet laying angle of the present invention just can be done very greatly, and this reduces many with regard to the cornerite that makes impeller blade; Make impeller cast than be easier to, pump efficiency also increases.
2. another innovation of the present invention is: entry guide vane is housed before the first stage impeller, and the outlet laying angle of entry guide vane blade is less than 50 degree.
Existing multistage centrifugal pump does not have entry guide vane at first stage impeller as last, and individual pump has entry guide vane, is in order to prevent the flow rotation yet, and its outlet laying angle is far longer than 50 degree.The present invention has increased an entry guide vane before first stage impeller, and its outlet laying angle just can make the flow that gets into first stage impeller that bigger rotational speed is also arranged, thereby make first stage impeller that the total head characteristic also arranged less than 50 degree.
Adopt the entry guide vane of outlet laying angle, not only can make the total head characteristic of multistage centrifugal pump better, and can make single stage centrifugal pump also have the total head function less than 50 degree.So this invention not only can be used for multistage centrifugal pump, also can be used for single stage centrifugal pump.
The invention has the beneficial effects as follows; Low specific speed multistage centrifugal pump and low specific speed single stage centrifugal pump with manufacturing of the present invention all have the total head characteristic; Not only can under high-lift low flow rate condition, high-efficiency reliable use, can also guarantee the overload free use of safety under the low lift and large flow rate operating mode of this pump.And low specific speed impeller of the present invention casting is than being easier to, and pump efficiency is also than higher.
Description of drawings
Below in conjunction with accompanying drawing and embodiment the present invention is further specified.
Fig. 1 is an one embodiment of the invention---well is with the axial plane sectional view of submersible pump.
Fig. 2 is the return guide vane blade figure of one embodiment of the invention.
Fig. 3 is the entry guide vane blade figure of one embodiment of the invention.
Fig. 4 is an another embodiment of the present invention---the axial plane sectional view of mining diving pump.
Fig. 5 is another embodiment of the present invention---the axial plane sectional view of single stage centrifugal pump.
Among the figure: 1. submersible motor connects seat, 2. running shaft, 3. water pump water inlet joint, 4. entry guide vane; 5. entry guide vane blade, 6. impeller, 7. blower inlet casing, 8. return guide vane blade; 9. water pump water outlet parts, the 10. outlet laying angle of return guide vane blade, the outlet laying angle of 11. entry guide vane blades.
Embodiment
Fig. 1 be the present invention at well with the embodiment in the submersible pump; It is composed in series impeller 6 and blower inlet casing 7 by many; Its impeller 6 is receded disk impellers, and its blower inlet casing 7 contains return guide vane blade 8, and the current of pumping get into impeller 6 imports through return guide vane blade 8; Itself and existing well with the difference of submersible pump be the outlet laying angle 10 of return guide vane blade less than 50 degree, this can see very clearly in Fig. 2.Another innovation of the present invention is: entry guide vane 4 is arranged before the first stage impeller, and the outlet laying angle 11 of entry guide vane blade 5 is less than 50 degree, and this can see very clearly in Fig. 3.
In this embodiment; Water pump water inlet joint 3 connects seat 1 with submersible motor and is bound up; 4 impellers 6 all are contained on the running shaft 2, and when 6 rotations of running shaft 2 impeller, the water in the motor-pumped well will be through water inlet joint 3 and entry guide vane 4; Get into impeller 6 again, get water pump from water pump water outlet parts 9 at last.The flow that from motor-pumped well, gets into water inlet joint 3 is non-rotary; The flow that gets into entry guide vane 4 from water inlet joint 3 also is non-rotary; But rotate from the flow that entry guide vane 4 gets into impeller 6; Because the outlet laying angle 11 of entry guide vane blade 5 is less than 50 degree, and its rotational speed is directly proportional with flow, this and do not have the existing water pump of entry guide vane 4 that a great difference is arranged.Because the lift of impeller is to improve with the rotational speed of impeller inlet flow to reduce, the flow of existing water pump entering first stage impeller is not rotated basically, so the lift of impeller is than higher, and its pump power is bigger naturally.But the flow rotational speed of present embodiment impeller inlet increases with flow, and the lift of therefore big flow operating mode is lower, and its pump power is also lower, and water pump just can not overload because flow increases yet.When impeller 6 is got impeller to water; The flow rotational speed is very big; The return guide vane blade 8 of blower inlet casing 7 is used for changing into the flow of high speed rotating the current of low-speed motion, because the outlet laying angle 10 of the return guide vane blade of present embodiment is less than 50 degree, so the flow that gets into next stage impellers 6 through return guide vane blade 8 remains rotation; Only its rotational speed is smaller, and reduces and littler with flow.Because low specific speed centrifugal pump is mainly used in high-lift small flow; Therefore at specified applying working condition, its lift and existing water pump are similar, but in big flow operating mode; Its flow circumferential speed component that gets into next stage impeller 6 through return guide vane blade 8 can be very big; Therefore the lift reduction is also very big, and this just greatly reduces the water-horse power of big flow operating mode, and water pump just can not overload because flow increases yet.The outlet laying angle of existing multistage centrifugal pump return guide vane blade is generally got about 80 degree; Minimum can be less than 55 degree yet; Though get into the flow of next stage impeller from blower inlet casing some circumferential speed component are arranged also, circumferential speed component is too little, reduces also very little to big flow lift; The water-horse power of therefore big flow operating mode is very big, causes the pump power overload.
Because getting into the velocity vector of impeller inlet, present embodiment has bigger circumferential speed component; Therefore the impeller inlet laying angle just can do more; This reduces many with regard to the cornerite that makes impeller blade, make impeller cast than be easier to, and pump efficiency also increases.
Fig. 4 is the embodiment of the present invention at mining diving pump, and its mode of execution and well are basic identical with submersible pump.Fig. 5 is the embodiment of the present invention at single stage centrifugal pump, and its entry guide vane blade 5 is more convenient with axial installation, and the outlet laying angle 11 of its entry guide vane blade is also less than 50 degree.

Claims (2)

1. total head centrifugal pump; Be composed in series by one or more pairs of impellers and blower inlet casing, its impeller is a receded disk impeller, and its blower inlet casing contains the return guide vane blade; The current of pumping get into impeller inlet through the return guide vane blade, it is characterized in that: the outlet laying angle of return guide vane blade is less than 50 degree.
2. a kind of total head centrifugal pump as claimed in claim 1 is characterized in that: entry guide vane is housed before the first stage impeller, and the outlet laying angle of entry guide vane blade is less than 50 degree.
CN2011103063992A 2011-09-28 2011-09-28 Full-lift centrifugal pump Pending CN102392832A (en)

Priority Applications (2)

Application Number Priority Date Filing Date Title
CN2011103063992A CN102392832A (en) 2011-09-28 2011-09-28 Full-lift centrifugal pump
PCT/CN2012/079141 WO2013044675A1 (en) 2011-09-28 2012-07-25 Full-lift centrifugal pump

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
CN2011103063992A CN102392832A (en) 2011-09-28 2011-09-28 Full-lift centrifugal pump

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WO (1) WO2013044675A1 (en)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN102878091A (en) * 2012-10-11 2013-01-16 江苏大学 Method for determining centrifugal pump full-condition theoretical lifts based on internal flow measurement
WO2013044675A1 (en) * 2011-09-28 2013-04-04 江苏大学 Full-lift centrifugal pump
CN106122081A (en) * 2016-08-16 2016-11-16 台州锦霸工贸有限公司 A kind of impeller assembly in deep well pump

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN108869317A (en) * 2018-06-22 2018-11-23 湖南天奥星泵业有限公司 It is a kind of connect fore pump main pump add hydraulic recycling turbine unit and its design method
CN110159595A (en) * 2019-05-29 2019-08-23 江苏大学 A kind of multistage pump return guide vane increasing runner and runner increase method
CN111966956B (en) * 2020-08-25 2024-01-26 河北省水资源研究与水利技术试验推广中心 Method for calculating lift and flow of multi-stage submersible pump for well
CN116085248A (en) * 2023-03-16 2023-05-09 山东鑫海矿业技术装备股份有限公司 Mining double-stage pump with protection function

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US3986791A (en) * 1974-04-01 1976-10-19 Sigma Lutin, Narodni Podnik Hydrodynamic multi-stage pump
SU1726851A1 (en) * 1990-04-26 1992-04-15 Производственное объединение "Невский завод" им.В.И.Ленина Intermediate stage of centrifugal compressor
CN1786479A (en) * 2005-12-13 2006-06-14 江苏大学 Centrifugal pump for deep well
CN201027656Y (en) * 2006-09-19 2008-02-27 邹节廉 Speed-adjusting main feed pump of energy-saving hydraulic coupler
CN201568310U (en) * 2009-09-11 2010-09-01 上海凯泉泵业（集团）有限公司 Stainless steel barrel-shaped horizontal multistage centrifugal pump
CN202417951U (en) * 2011-09-28 2012-09-05 江苏大学 Total-head centrifugal pump

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CN101639085A (en) * 2008-08-01 2010-02-03 清华大学 Energy-saving device and energy-saving method by regulating front guide vanes of centrifugal pump
EP2542784B1 (en) * 2010-03-05 2019-05-08 Weir Minerals Australia Ltd Pump intake device
CN102392832A (en) * 2011-09-28 2012-03-28 江苏大学 Full-lift centrifugal pump

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3986791A (en) * 1974-04-01 1976-10-19 Sigma Lutin, Narodni Podnik Hydrodynamic multi-stage pump
SU1726851A1 (en) * 1990-04-26 1992-04-15 Производственное объединение "Невский завод" им.В.И.Ленина Intermediate stage of centrifugal compressor
CN1786479A (en) * 2005-12-13 2006-06-14 江苏大学 Centrifugal pump for deep well
CN201027656Y (en) * 2006-09-19 2008-02-27 邹节廉 Speed-adjusting main feed pump of energy-saving hydraulic coupler
CN201568310U (en) * 2009-09-11 2010-09-01 上海凯泉泵业（集团）有限公司 Stainless steel barrel-shaped horizontal multistage centrifugal pump
CN202417951U (en) * 2011-09-28 2012-09-05 江苏大学 Total-head centrifugal pump

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2013044675A1 (en) * 2011-09-28 2013-04-04 江苏大学 Full-lift centrifugal pump
CN102878091A (en) * 2012-10-11 2013-01-16 江苏大学 Method for determining centrifugal pump full-condition theoretical lifts based on internal flow measurement
CN102878091B (en) * 2012-10-11 2015-04-22 江苏大学 Method for determining centrifugal pump full-condition theoretical lifts based on internal flow measurement
CN106122081A (en) * 2016-08-16 2016-11-16 台州锦霸工贸有限公司 A kind of impeller assembly in deep well pump

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Application publication date: 20120328