CN106351881A - External mixing type self-priming centrifugal pump - Google Patents
External mixing type self-priming centrifugal pump Download PDFInfo
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- CN106351881A CN106351881A CN201610853890.XA CN201610853890A CN106351881A CN 106351881 A CN106351881 A CN 106351881A CN 201610853890 A CN201610853890 A CN 201610853890A CN 106351881 A CN106351881 A CN 106351881A
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- spiral case
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- 239000007788 liquid Substances 0.000 claims abstract description 56
- 238000000926 separation method Methods 0.000 claims abstract description 30
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 claims description 11
- 241000237858 Gastropoda Species 0.000 claims description 3
- 238000010992 reflux Methods 0.000 abstract 12
- 238000005516 engineering process Methods 0.000 description 5
- 230000008676 import Effects 0.000 description 5
- 230000037452 priming Effects 0.000 description 5
- 238000010586 diagram Methods 0.000 description 4
- 230000000694 effects Effects 0.000 description 4
- 238000000034 method Methods 0.000 description 4
- 230000006378 damage Effects 0.000 description 3
- 238000009826 distribution Methods 0.000 description 3
- 239000012530 fluid Substances 0.000 description 3
- 210000004907 gland Anatomy 0.000 description 3
- 239000000203 mixture Substances 0.000 description 3
- 230000008569 process Effects 0.000 description 3
- 230000010349 pulsation Effects 0.000 description 3
- 238000010521 absorption reaction Methods 0.000 description 2
- 230000009286 beneficial effect Effects 0.000 description 2
- 230000008901 benefit Effects 0.000 description 2
- 230000008859 change Effects 0.000 description 2
- 230000006872 improvement Effects 0.000 description 2
- 238000003973 irrigation Methods 0.000 description 2
- 230000002262 irrigation Effects 0.000 description 2
- 238000005381 potential energy Methods 0.000 description 2
- 238000005086 pumping Methods 0.000 description 2
- 239000002096 quantum dot Substances 0.000 description 2
- 238000007789 sealing Methods 0.000 description 2
- 238000005303 weighing Methods 0.000 description 2
- 241001503485 Mammuthus Species 0.000 description 1
- 230000009471 action Effects 0.000 description 1
- 230000004323 axial length Effects 0.000 description 1
- 230000033228 biological regulation Effects 0.000 description 1
- 150000001875 compounds Chemical class 0.000 description 1
- 230000008878 coupling Effects 0.000 description 1
- 238000010168 coupling process Methods 0.000 description 1
- 238000005859 coupling reaction Methods 0.000 description 1
- 230000007812 deficiency Effects 0.000 description 1
- 238000004141 dimensional analysis Methods 0.000 description 1
- 239000006260 foam Substances 0.000 description 1
- 230000005484 gravity Effects 0.000 description 1
- 238000009434 installation Methods 0.000 description 1
- 230000003993 interaction Effects 0.000 description 1
- 210000001503 joint Anatomy 0.000 description 1
- 238000012423 maintenance Methods 0.000 description 1
- 238000011089 mechanical engineering Methods 0.000 description 1
- 238000005272 metallurgy Methods 0.000 description 1
- 210000002445 nipple Anatomy 0.000 description 1
- 238000012856 packing Methods 0.000 description 1
- 239000011148 porous material Substances 0.000 description 1
- 238000004321 preservation Methods 0.000 description 1
- 238000004088 simulation Methods 0.000 description 1
- 238000003860 storage Methods 0.000 description 1
- 230000007704 transition Effects 0.000 description 1
Classifications
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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
- 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
-
- 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
- F04D29/66—Combating cavitation, whirls, noise, vibration or the like; Balancing
- F04D29/669—Combating cavitation, whirls, noise, vibration or the like; Balancing especially adapted for liquid pumps
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D9/00—Priming; Preventing vapour lock
- F04D9/004—Priming of not self-priming pumps
- F04D9/005—Priming of not self-priming pumps by adducting or recycling liquid
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D9/00—Priming; Preventing vapour lock
- F04D9/004—Priming of not self-priming pumps
- F04D9/006—Priming of not self-priming pumps by venting gas or using gas valves
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Life Sciences & Earth Sciences (AREA)
- Sustainable Development (AREA)
- Structures Of Non-Positive Displacement Pumps (AREA)
Abstract
The invention provides an external mixing type self-priming centrifugal pump. A first reflux hole and a second reflux hole are formed in two symmetrical sides of the middle section of an impeller respectively; an inner cavity of a volute communicates with the right side of a gas-liquid separation chamber through the first reflux hole and also communicates with the left side of the gas-liquid separation chamber through the second reflux hole, a pump cover through hole, a diversion tube and a drain hole, and the pump cover through hole is formed in a pump cover, and the drain hole is formed in the gas-liquid separation chamber; the distance between a right end opening of the first reflux hole and the middle section of the impeller is equal to that between a left end opening of the second reflux hole and the middle section of the impeller; the cross section of the first reflux hole and the cross section of the second reflux hole are both in an elliptical shape. The connection line between the first circle center and the second circle center is defined as a reflux hole position line, the middle point of the reflux hole position line is located in the plane of the middle section of the impeller, the radial direction, where the middle point is located, of the middle section of the impeller is defined as the position radial direction, and the direction of the short axis of the cross section of the first reflux hole and the direction of the short axis of the cross section of the second reflux hole are both parallel to the position radial direction.
Description
Technical field
The present invention relates to a kind of exterior mixing self-priming centrifugal pump.
Background technology
External-mix self-priming pump belongs to one kind of centrifugal pump, because of its good self-priming performance and job stability, widely should
For fields such as agricultural drainage and irrigation, municipal blowdown, petrochemical industry metallurgy and food chemistries.Compared with Ordinary Centrifugal Pumps, on the self priming pump pump housing
There is backflow pore structure.When return port can ensure that self-priming pump startup, liquid is flowed back and introduces spiral case, so that gas-liquid is fully mixed
Close, gas-liquid mixed is discharged spiral case and entered gas-liquid separation chamber by impeller acting, and gas is discharged along outlet, and the larger liquid of proportion is then
Sink to separation chamber bottom, turn again to spiral case through return port, with gas mixing, so circulation is until draining in intake line
Gas, thus realize self-priming.
But, after self priming pump normal work, the backflow effect of pump housing upper return port has a strong impact on the flowing in spiral case
State, under the backflow of return port with the comprehensive function of impeller-spiral case stator-rotor interaction, the flowing in spiral case is increasingly complex.Through returning
The liquid that discharge orifice is back in spiral case destroys in spiral case symmetrically fluidal texture, makes to produce week in time in spiral case cross section
The unilateral spiral structure of phase change, not only causes hydraulic loss in spiral case to increase, also can induce serious pressure fluctuation, cause machine
Group vibration and noise.And, due to its impact to impeller for one side backflow, axial force of impeller can significantly increase, and seriously reduces axle
The service life held, makes impeller that axial float occurs it is more likely that causing impeller port ring to wear and tear simultaneously.
Content of the invention
For solving above technological deficiency, the present invention proposes a kind of exterior mixing self-priming centrifugal pump pump body structure, makes spiral case both sides
Symmetrical backflow, can improve the flow regime in spiral case, make to produce the metastable flowing being symmetrical in impeller middle section in spiral case
Structure, thus reducing hydraulic loss, reduces pressure fluctuation, and the axial force of impeller causing that symmetrically flows back can be cancelled out each other, from
And greatly improve stability and the reliability of self priming pump operating.
The technical scheme is that
A kind of exterior mixing self-priming centrifugal pump, the centrifugal pump being vertically arranged includes the pump housing in left side and the pump cover on right side, the pump housing
It is arranged on the pump support of level, the pump housing is provided with the pump discharge of suction chamber into water and draining, is provided with impeller, spiral case in the pump housing
And gas-liquid separation chamber, and impeller is arranged in spiral case；Pump shaft runs through pump cover, and the left end of pump shaft extends in spiral case, and impeller is fixed
On the left end of pump shaft, the right-hand member of pump shaft is connected with the output shaft of motor；Suction chamber is connected with the entrance of impeller, the going out of impeller
Mouthful be connected with volute inlet, the outlet of spiral case is connected with gas-liquid separation chamber, gas-liquid separation chamber by pump discharge to exterior liquid,
Aerofluxuss；
First return port and the second return port are had on described spiral case, the first return port and the second return port are located at leaf respectively
The symmetrical both sides in wheel middle section；Spiral case inner chamber is connected with the right side of gas-liquid separation chamber by the first return port, and spiral case inner chamber is successively
Connected with the left side of gas-liquid separation chamber by the second return port, pump cover through hole, mozzle, osculum, pump cover through hole is opened in pump
Cover, osculum is opened in gas-liquid separation chamber；The right-end openings of the first return port are connected with spiral case inner chamber, the second return port
Left end opening is connected with spiral case inner chamber, and the distance between the right-end openings of the first return port and impeller middle section and the second backflow
The distance between the left end opening in hole and impeller middle section are equal；Described impeller middle section refers to impeller center vertically
The cross section that place is located；The shape of the cross section of the cross section of the first return port and the second return port is ellipse.
With the center of circle of the cross section at the right-end openings place of the first return port for first center of circle, with the left end of the second return port
The center of circle of the cross section that opening is located is second center of circle, and defining first center of circle and the line in second center of circle is the return port position line,
Then the midpoint of the return port position line is located in the plane that impeller middle section is located, and defines the impeller middle section that described midpoint is located
Be radially position radial direction, then the short axle place side of the short axle place direction of the first return port cross section and the second return port cross section
Position described in Xiang Junyu is radially parallel.
Further, described suction chamber is in vertically s shape, and the entrance of suction chamber passes through intake line with external source even
Logical, the outlet of suction chamber is connected with the entrance of impeller, and the axis of suction chamber porch cross section is higher than the outlet of spiral case.
Further, the first return port, the center of circle of the cross section of the second return port, pump cover through hole and osculum are in same level
On line, to ignore the impact of potential energy.
Further, the axis of described pump discharge and the axis of volute outlet coincide.
Further, cut water and the return port position line are 3.3～3.8rad along the angle theta of impeller direction of rotation.
Further, the length of the short axle of the first return port cross section is the 40%～60% of long axis length, the second return port
The length of the short axle of cross section be the 40%～60% of long axis length.
The invention has the beneficial effects as follows:
1. symmetrically flow back in both sides of the present invention, changes the asymmetry quantum dot structure of mechanical periodicity in time in spiral case, both sides
Symmetrical backflow makes the fluidal texture in spiral case tend to symmetrical, and flow regime in the improvement spiral case of high degree reduce inter alia snail
Vortex motion structure in shell, reduces hydraulic loss.
2. symmetrically flow back in both sides of the present invention, makes the pressure distribution in spiral case more uniform, improves in spiral case section simultaneously
Mechanical periodicity in time asymmetric Secondary Flow, it is possible to decrease pressure fluctuation, improve pump operation stability.
3. symmetrically flow back in both sides of the present invention, and the axial force of impeller caused by impact impeller can be cancelled out each other, with prior art
Axial force of impeller compare and substantially reduce, the impact to bearing and mechanical seal can be reduced, increase its service life, avoid simultaneously
The harm that impeller axial float is brought.
4 present invention drain by the way of mozzle, easy to use, with low cost, reaching the same of symmetrical backflow purpose
When do not have increase pump body structure complexity, will not increase its cast difficulty.
5. the present invention ensures, by way of certain altitude difference, to save import check valve by suction chamber import and volute outlet
Install, both reduced cost, the external characteristics of pump can be improved again.
Brief description
Fig. 1 is the sectional view of the present invention.
Fig. 2 is structure enlarged diagram at b in Fig. 1.
Fig. 3 is structure enlarged diagram at c in Fig. 1.
Fig. 4 is the first backflow hole site schematic shapes.
Fig. 5 is the isometric side view of the present invention.
Fig. 6 a be prior art exterior mixing self-priming centrifugal pump at return port spiral case section motion pattern；
Fig. 6 b is the section motion pattern of present invention spiral case at the first return port and the second return port.
Fig. 7 is pressure fluctuation time domain pair in the exterior mixing self-priming centrifugal pump of prior art and present invention spiral case at return port
Ratio figure, the longitudinal axis c of in figurepCharacteristic for pressure fluctuation.
Fig. 8 is pressure fluctuation frequency domain pair in the exterior mixing self-priming centrifugal pump of prior art and present invention spiral case at return port
Ratio figure, the longitudinal axis c of in figurepCharacteristic for pressure fluctuation.
Fig. 9 is the exterior mixing self-priming centrifugal pump of prior art and the axial force of impeller comparison diagram of the present invention.
In figure: the 1- pump housing, 2- suction chamber, 3- spiral case, 4- impeller, 5- flat key, 6- the impeller nut, (storage of 7- gas-liquid separation chamber
Liquid room), 8- the second return port two, 9- first return port, 10- mozzle, 11- pump support, 12- steam vent, 13- pump discharge, 14-
Volute outlet, 15- pump cover, 16- first bolt, 18- second bolt, 21- the 3rd bolt, 19- front axle pressure cap, bearing after 20-
Gland, 22- pump shaft, 23- heel row bearing, 24,25- front row bearing, 26- rubber ring, 27- mechanical seal, 28- pump cover through hole, 29-
Union joint, 30- clamp nut, 31- packing ring, 32- cut water.
Specific embodiment
The present invention is further described with reference to the accompanying drawings and examples.
As illustrated, a kind of exterior mixing self-priming centrifugal pump, the centrifugal pump being vertically arranged includes the pump housing 1 in left side and right side
Pump cover 15, the pump housing 1 is arranged on the pump support 11 of level, and the pump housing 1 is provided with the pump discharge 13 of suction chamber 2 into water and draining,
It is provided with impeller 4, spiral case 3 and gas-liquid separation chamber 7 in the pump housing 1, and impeller 4 is arranged in spiral case 3；Pump shaft 22 runs through pump cover 15, pump
The left end of axle 22 extends in spiral case 3, and impeller 4 is fixed on the left end of pump shaft 22, the right-hand member of pump shaft 22 and the output shaft of motor
It is connected；Suction chamber 2 is connected with the entrance of impeller 4, and the outlet of impeller 4 is connected with spiral case 3 entrance, the outlet of spiral case 3 and gas
Liquid separation chamber 7 is connected, and gas-liquid separation chamber 7 passes through pump discharge 13 to exterior liquid；
First return port 9 and the second return port 8 are had on described spiral case 3, the first return port 9 and the second return port 8 are respectively
Positioned at the symmetrical both sides in impeller middle section；Spiral case 3 inner chamber is connected with the right side of gas-liquid separation chamber 7 by the first return port 9, spiral case
3 inner chambers pass sequentially through the second return port 8, pump cover through hole 28, mozzle 10, osculum are connected with the left side of gas-liquid separation chamber 7, pump
Lid through hole 28 is opened on pump cover 15, and osculum is opened in gas-liquid separation chamber 7；First time
The right-end openings of discharge orifice 9 are connected with spiral case 3 inner chamber, and the left end opening of the second return port 8 is connected with spiral case 3 inner chamber,
And first return port 9 the distance between right-end openings and impeller middle section and the left end opening and impeller of the second return port 8 in
The distance between section is equal；Described impeller middle section refers to the cross section that impeller 3 center vertically is located；First
The shape of the cross section of the cross section of return port 9 and the second return port 8 is ellipse.
With the center of circle of the cross section at the right-end openings place of the first return port 9 for first center of circle, with a left side for the second return port 8
The center of circle of the cross section that end opening is located is second center of circle, and defining first center of circle and the line in second center of circle is backflow hole site
Line, then the midpoint of the return port position line be located in the plane that impeller middle section is located, define in the impeller that described midpoint is located and cut
The radial direction in face is position radial direction, then the short axle of the short axle place direction of the first return port 9 cross section and the second return port 8 cross section
All radially paralleled with described position in place direction.
The short axle of the short axle place direction of the first return port 9 cross section and the second return port 8 cross section and position radial direction phase
Parallel, the stress concentration that the first return port 9 and two return port 8 perforate bring to spiral case 3 can be reduced, also can reduce backflow to snail
The impact of main flow in shell 3.
The length of the short axle of the first return port 9 cross section is the 40%～60% of long axis length, the second return port 8 transversal
The length of the short axle in face is the 40%～60% of long axis length.The length range of short-axis direction is controlled with this, if the first return port 9
All oversized along its cross section short-axis direction with the second return port 8, spiral case at the first return port 9 and the second return port 8 can be made
In cross section, large area is affected, and increases hydraulic loss.
Cut water and the return port position line are 3.3～3.8rad along the angle theta of impeller direction of rotation, and return port center is in this model
When enclosing interior, the self-priming performance of pump is best.
Described suction chamber 2 is in vertically s shape, and the entrance of suction chamber 2 is connected with external source by intake line, inhales
The outlet of hydroecium 2 is connected with the entrance of impeller 4, and the axis of suction chamber 2 porch cross section is higher than the outlet of spiral case 14.
First return port 9, the center of circle of the cross section of the second return port 8, pump cover through hole 28 and osculum are in same horizontal line
On, to ignore the impact of potential energy.
The axis that the axis of described pump discharge 13 is exported with spiral case 14 coincides, to ensure the smooth efflux pump of liquid
Outward, reduce hydraulic loss.
Both sides of the present invention are symmetrical arranged the first return port and the second return port, change in spiral case 3 mechanical periodicity in time
Asymmetry quantum dot structure, the symmetrical backflow in both sides makes the fluidal texture in spiral case tend to symmetrical, in the improvement spiral case of high degree
Flow regime, reduce inter alia the vortex motion structure in spiral case, reduces hydraulic loss.Especially when both sides symmetrical capacity of returns phase
Deng when, symmetrical reflowing result becomes apparent from.
But because mozzle 10 has certain energy loss in drainage process, for ensureing the first return port 9 and second
The capacity of returns of return port 8 is identical, and the area outline of the cross section of the second return port is less than the area of the cross section of the first return port,
And the cross-sectional area a when the first return port 9k1Area a with the cross section of the second return portk2When meeting following formula respectively:
Can guarantee that the first return port 9 is identical with the capacity of returns of the second return port 8, in formula, n is specified turn of self priming pump
Speed, unit is r/min；d2For impeller outer diameter, unit is m；qdFor the flow of self priming pump, unit is m3/h；D is the straight of mozzle
Footpath, unit is m；d≈1.2dk1, dk1Equivalent diameter for the first return port 9；L is the length of mozzle 10, and unit is m；δ is
The axial length of the second return port 8, unit is m；θ is cut water along impeller direction of rotation to the radian at return port center, value model
Enclose 3.3～3.8rad；λ is mozzle frictional resistant coefficient.
Because current can have energy loss, the cross-sectional area a of the second return port 8 in mozzle 10k2Can not be direct
Cross-sectional area a equal to the first return port 9k1, to try to achieve ak2, first have to calculate the energy loss that mozzle 10 leads to, with logical
Cross preservation of energy and mass conservation law asks for ak2And ak1.Hydraulic pressure at the first return port 9 and the second return port 8 for the definition
For lateral pressure, liquid mean flow rate at the first return port 9 or the second return port 8 for the definition is side speed, then gas-liquid separation
Room 7 inside pressure is p1, liquid separation chamber 7 inner side speed is v1；Spiral case inside pressure is pv, inside spiral case, speed is vv；First time
Liquid mean flow rate in discharge orifice 9 is vk1.As follows to the first return port 9 both sides row Bernoulli equation first:
Wherein, ξ1It is the resistance coefficient of the first return port 9, ρ is the density of liquid, g=9.8n/kg.
Cross-sectional area a according to the first return portk1And its shape determines mozzle 10 diameter d, take d=1.2dk1, dk1For
The equivalent diameter of the first return port 9, water conservancy diversion length of tube l determines according to the size of the pump housing.If liquid mean flow rate in mozzle 10
For v, the second backflow in the hole liquid mean flow rate is vk2, equivalent diameter d of the second return portk2.To mozzle 10 import and second
Return port 8 exports row Bernoulli equation, and (one end that definition mozzle is connected with pump cover through hole is mozzle import, defines second time
One end that discharge orifice is connected with pump cover through hole is the second backflow hole exits):
Wherein, ξ2Resistance coefficient for draft tube outlets and pump cover through hole 28 junction；ξ3Export resistance for the second return port 8
Force coefficient；λ is mozzle frictional resistant coefficient；Due to now dk2Unknown, solve equation (2) considerably complicated it is contemplated that dk2With d chi
Very little close, therefore approx take dk2=d.
If the capacity of returns of the first return port 9 and the second return port 8 is equal, had by the conservation of mass:
vk1·ak1=vk2·ak2(3)
By the first return port 9 flow velocity vk1, liquid viscosity coefficient calculates Reynolds in mozzle 10 diameter d and mozzle 10
Number, consults Moody chart further according to Reynolds number size and can obtain frictional resistant coefficient λ in mozzle 10, in inquiry fluid handbook
Coefficient of partial resistance table obtains: ξ1=0.06, ξ2=0.07, ξ3=1, formula (1) (2) is substituted into after formula (3), and according to pressure
Linear increase rule at cut water to return port for the power, then by ξ1=0.06, ξ2=0.07, ξ3=1 brings into and solves:
Prior art (referring to document: instrument group. the external-mix self-priming pump backflow budget of hole area and the determination of parameter. " irrigation and drainage
Mechanical engineering journal ", the 1992, the 1st phase, page 1～5) disclosed in return port computing formula be:
ak=(0.95～2.54) (n/q)2/3(4)
But formula (4) is only applicable to the situation of the single return port of calculating and setting, and 0.95～2.54 span phase
Difference is also larger, and does not consider the impact of geometric parameter d2.The present invention is provided with the first return port 9 and the second return port 8 two returns
Discharge orifice, formula (4) is simultaneously inapplicable.
Accordingly, it would be desirable to be modified to this formula on the basis of formula (4), adjust correlation coefficient, drawing can be accurate
Calculate the formula of the cross-sectional area of the first return port 9.Wherein, the first return port size ak1Main and parameter d2、qdWith n phase
Close, calculate through dimensional analysis and parameters weighing factor and understand, ak1Main and parameter d2、qdRelated with n, through dimension
Analysis and parameters weighing factor calculate, ak1With n-0.62、 It is directly proportional, transversal when the first return port 9
AreaWhen, the first return port 9 ensure the present invention work when flow and effect
Moreover it is possible to meet self-priming performance and suction lift under the premise of rate.
Operationally, the effect of mozzle 10 is to the second return port 8 drain to the present invention, improves flow regime in spiral case；
When needing draining or dismounting maintenance after termination of pumping, unload the connection of mozzle 10 and pump cover 15, you can discharge opeing.
Pump cover 15 not only serves the sealing function of traditional pump cover, and the pump cover through hole 28 arranging thereon can UNICOM's mozzle
With the second return port 8.First boss to be reserved when making for pump cover through hole 28, at the equally described pump housing 1 and pump cover 15 cooperation
Second boss to be reserved, the second return port 8 is got through at second boss.
Described bearing body 17 and pump cover 15 are connected, and the location dimension that bearing body 17 is coordinated with pump cover 15 can not be excessive, give
Pump cover through hole 28 headspace surplus.
The described pump housing 1 is connected by the first bolt 16 with pump cover 15, and pump cover 15 and bearing body 17 pass through the second bolt 18 phase
Even；Impeller 4 is located in spiral case 3, and described impeller 4 passes through flat key 5 and impeller nut 6 is connected in the left end of pump shaft 22；Described machinery
Sealing 27 is located between impeller 4 and pump cover 15, and described mechanical seal 27 is connected on pump shaft 22；Before being provided with described bearing body 17
Row's bearing 24,25 and heel row bearing 23, described front row bearing 24,25 and heel row bearing 23 are separately fixed at pump shaft 22 shaft shoulder two
Side；Described front axle pressure cap 19 and rear bearing gland 20 are fixed on bearing body 17 by the 3rd bolt 21, interspersed on pump shaft 22
There are impeller 4, mechanical seal 27, pump cover 15, front axle pressure cap 19, rear bearing gland 20, front-seat bearing 23,24 and heel row bearing
25, described pump shaft 22 right-hand member is connected with motor by shaft coupling.The import of described suction chamber 2 is without installation check valve, suction chamber
The axis of porch cross section exceeds 20mm～30mm than volute outlet 14 it is therefore intended that in the situation not installing check valve
Under, sufficiently high liquid level can be contained in gas-liquid separation chamber 7 during termination of pumping, being again started up during the present invention also can smoothly reaching self-priming will
Ask, it is to avoid the loss of check valve, improve the performance of pump.
Described mozzle 10 selects anti-riot connecting tube, and the big and bent characteristic of its intensity is convenient to be operated, mozzle 10
Left end is connected with the osculum on the pump housing 1, and the right-hand member of mozzle 10 is connected with the pump cover through hole 28 on pump cover 15, mozzle 10 with
The mode that osculum, mozzle 10 are connected with pump cover through hole 28 is identical, so that mozzle 10 is connected with osculum as a example, connected mode
For: mozzle 10 is connected with osculum by joint 29, and joint 29 is double nipple, and joint 29 right-hand member and the pump housing 1 are with screw thread
M22 × 1.5 coordinate, and butt joint 29 inner circle exit carries out chamfering, to reduce hydraulic loss；The left end of joint 29 and mozzle
10 clamp nut 30 is coordinated with screw thread m24 × 1.5, and seam cushioning circle 31 prevents leakage, clamp nut 30 and joint 29
Tighten and mozzle 10 can be compressed with joint 29, as shown in Figure 3.
Entrance due to suction chamber 2 ensure that certain difference in height with volute outlet 14, and when shutting down every time, liquid flows backwards not
Fully, the liquid of q.s can be stored in the pump housing 1, use for starting next time.Before initial start-up, foot need to be injected into the pump housing 1
The liquid of enough amounts, is started motor, is rotated by pump shaft 22 impeller 4, and the impeller 4 of high-speed rotation does work to its internal liquid,
Liquid is exported along impeller 4 by centrifugal force and flows into spiral case 3, and forms foam banding gas-liquid mixture with gas mixing, and gas-liquid is mixed
Compound slows down through spiral case 3 diffuser and is pressurized and is discharged to gas-liquid separation chamber 7.Now, because space increases suddenly, flow velocity rapid drawdown,
The little gas of relative density escapes from water along outside pump discharge 13 excavationg pump, and the larger liquid of relative density is fallen by action of gravity
To gas-liquid separation chamber 7 bottom, it is back in spiral case 3 through symmetrically arranged first return port 9 and the second return port 8, again with gas
Body mixes.The circulation going round and beginning again with said process, increasing gas is discharged, and the vacuum in suction chamber 2 constantly increases
Greatly, by conveying liquid, the suction tube that continuous edge is connected with suction chamber 2 is risen, be ultimately inhaled in pipe gas by emptying, the present invention
Complete self-priming process.
After the present invention completes to start, during normal operation, symmetrically arranged first return port 9 of the present invention and the second return port
8 just embody its advantage.When the present invention runs well, the pressure in gas-liquid separation chamber 7 is higher than the pressure in spiral case 3,
So when yet suffer from flowing back, because the first return port 9 and the second return port 8 are symmetricly set on the both sides of impeller middle section, especially
It is when the first return port 9 is identical with the flow of the second return port 8 so that the fluidal texture in spiral case 3 is to be symmetrical in impeller 4
Middle section, mobile phase, to stable, can eliminate or reduce the secondary flow phenomenon in spiral case 3 section, therefore can reduce hydraulic loss,
Reduce pressure fluctuation.The symmetrical withdrawing fluid of the present invention, the axial force of impeller caused by impact impeller 4 can be cancelled out each other, with now
The axial force of impeller having technology is compared and is substantially reduced, and can increase bearing service life, avoids impeller axial float to be brought simultaneously
Harm.
The advantage that the cross section of the first return port 9 and the second return port 8 is ellipse is: contour line is to smoothly transit
Curve, its boundary layer flow even transition when liquid flows through the first return port 9 and the second return port 8, flowing stablize waterpower damage
Lose little.Facilitate determination and the regulation of the first return port 9 and the second return port 8 shape；First determine the first return port 9 and the second backflow
The cross-sectional area in hole 8, then determine the first return port 9 and the shape of the second return port 8；: determine horizontal taking the first return port 9 as a example
Sectional area ak1, in conjunction with spiral case 3 structure by area formula ak1=π ab gives half length of the oval cross section of the first return port 9
Axle b and semi-minor axis a, you can determine the shape of the first return port 9, wherein a are about the 40%～60% of b.Can be in the first return port 9
Carry out the rounding of 0.5～5mm according to the size of its own with the both sides of the second return port 8, damaged with the energy reducing current
Lose.
In order to definitely at large understand beneficial effects of the present invention, the exterior mixing self-absorption centrifugal to prior art respectively
Pump and the present invention have carried out numerical simulation, below for analog result and analysis:
Fig. 6 a is the section motion pattern of exterior mixing self-priming centrifugal pump of the prior art spiral case at return port；Fig. 6 b is this
The section motion pattern of invention spiral case 3 at the first return port and the second return port.By contrast it is found that of the prior art
, there are serious secondary flow vortices in the side relative with return port in spiral case in exterior mixing self-priming centrifugal pump, flow in spiral case section
Dynamic structure is asymmetrical, and this secondary flow structure changes in time, and pressure distribution is uneven, there is larger pressure ladder
Degree, return port lateral pressure is maximum, and the position occurring in vortex has obvious low-pressure area.And the present invention plants two in spiral case 3 section
Secondary stream vortex disappears, and both sides withdrawing fluid uniformly flows in spiral case 3, in centre because two bursts of backflows flow direction of meeting changes,
To impeller 4 Way out diffluence, whole fluidal texture is almost symmetrical in impeller middle section, and pressure distribution is similarly symmetrical, and leaf
First return port 9 of wheel middle section both sides and the second return port 8 arrive the uniform mistake of pressure near impeller 4 exit in the middle of spiral case 3
Cross.
Can be drawn by the comparison of Fig. 6 a and Fig. 6 b, the present invention significantly improves exterior mixing self-absorption centrifugal of the prior art
The uneven flow regime at return port of pump.
Fig. 7 is pressure fluctuation time domain in the exterior mixing self-priming centrifugal pump of prior art and present invention spiral case at return port
Figure；Fig. 8 is pressure fluctuation frequency domain figure in the exterior mixing self-priming centrifugal pump of prior art and present invention spiral case at return port, collection
Data is two impeller swing circles.Observe Fig. 7 discovery, the exterior mixing self-priming centrifugal pump of prior art and the spiral case of the present invention
At return port, pressure fluctuation time domain variation tendency is all consistent, assumes 2 pulsation periods, have crest, ripple in each swing circle
Each two of paddy, periodically pulsing is fairly obvious, but the pressure fluctuation in the present invention all slightly reduces.Observe Fig. 8 to find, existing
The ripple frequency of the exterior mixing self-priming centrifugal pump of technology and the present invention is all the blade passing frequency (96.67hz) and its again of impeller
Frequently, primary frequency zone is 1 times of leaf frequency, and secondary dominant frequency is 2 times of leaf frequencies, and the pulsation amplitude of high power leaf frequency is relatively weak.Under each frequency of the present invention
The exterior mixing self-priming centrifugal pump of pulsation amplitude hinge structure all decrease, primary frequency zone is more obvious, compares prior art
Reduce by 33.8%.
Fig. 9 is the exterior mixing self-priming centrifugal pump of prior art and the axial force of present invention impeller 4 in two swing circles
Schematic diagram.It can be found that the axial force of impeller 4 of the present invention substantially reduces compared with prior art, in impeller 4 swing circle, leaf
Take turns the meansigma methodss of 4 axial forces and the maximum range of decrease is respectively 51.1% and 47.6%.For mammoth pump, effect will be brighter
Aobvious.
Content described in this specification embodiment is only enumerating of the way of realization to inventive concept, the protection of the present invention
Scope is not construed as being only limitted to the concrete form that embodiment is stated, protection scope of the present invention also includes art technology
Personnel according to present inventive concept it is conceivable that equivalent technologies mean.
Claims (4)
1. a kind of exterior mixing self-priming centrifugal pump it is characterised in that: the centrifugal pump being vertically arranged includes the pump housing and the right side in left side
Pump cover, the pump housing is arranged on the pump support of level, and the pump housing is provided with the pump discharge of suction chamber into water and draining, is provided with the pump housing
Impeller, spiral case and gas-liquid separation chamber, and impeller is arranged in spiral case；Pump shaft runs through pump cover, and the left end of pump shaft extends in spiral case,
Impeller is fixed on the left end of pump shaft, and the right-hand member of pump shaft is connected with the output shaft of motor；Suction chamber is connected with the entrance of impeller,
The outlet of impeller is connected with volute inlet, and the outlet of spiral case is connected with gas-liquid separation chamber, and gas-liquid separation chamber passes through pump discharge
To exterior liquid, aerofluxuss；
First return port and the second return port are had on described spiral case, the first return port and the second return port are located in impeller respectively
The symmetrical both sides in section；Spiral case inner chamber is connected with the right side of gas-liquid separation chamber by the first return port, and spiral case inner chamber passes sequentially through
Second return port, pump cover through hole, mozzle, osculum are connected with the left side of gas-liquid separation chamber, and pump cover through hole is opened on pump cover,
Osculum is opened in gas-liquid separation chamber；The right-end openings of the first return port are connected with spiral case inner chamber, the left end of the second return port
Opening is connected with spiral case inner chamber, and the distance between the right-end openings of the first return port and impeller middle section and the second return port
The distance between left end opening and impeller middle section are equal；Described impeller middle section refers to impeller center place vertically
Cross section；The shape of the cross section of the cross section of the first return port and the second return port is ellipse.
With the center of circle of the cross section at the right-end openings place of the first return port for first center of circle, with the left end opening of the second return port
The center of circle of the cross section being located is second center of circle, and defining first center of circle and the line in second center of circle is the return port position line, then return
The midpoint of the discharge orifice position line is located at the radial direction defining the impeller middle section that described midpoint is located in the plane that impeller middle section is located
For position radially, then the short axle place direction of the short axle place direction of the first return port cross section and the second return port cross section is equal
Radially parallel with described position.
2. as claimed in claim 1 a kind of exterior mixing self-priming centrifugal pump it is characterised in that: described suction chamber is in vertically
S shape, the entrance of suction chamber is connected with external source by intake line, and the outlet of suction chamber is connected with the entrance of impeller, water suction
At chamber inlet, the axis of cross section is higher than the outlet of spiral case.
3. as claimed in claim 2 a kind of exterior mixing self-priming centrifugal pump it is characterised in that: the first return port, the second return port,
The center of circle of the cross section of pump cover through hole and osculum is in the same horizontal line.
4. as claimed in claim 3 a kind of exterior mixing self-priming centrifugal pump it is characterised in that: the axis of described pump discharge and snail
The axis of shell outlet coincides.
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| CN201610853890.XA CN106351881B (en) | 2016-09-27 | 2016-09-27 | A kind of exterior mixing self-priming centrifugal pump |
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| CN201610853890.XA CN106351881B (en) | 2016-09-27 | 2016-09-27 | A kind of exterior mixing self-priming centrifugal pump |
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| CN106351881B CN106351881B (en) | 2019-02-01 |
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Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
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| CN108194384A (en) * | 2017-12-21 | 2018-06-22 | 江苏双轮泵业机械制造有限公司 | A kind of centrifugal pump system |
| CN112643298A (en) * | 2020-12-25 | 2021-04-13 | 浙江燃创透平机械股份有限公司 | Flow guide pipe of gas turbine stationary blade in heat pump system and preparation method |
| GB2625470A (en) * | 2022-05-13 | 2024-06-19 | Bissell Inc | Surface cleaner |
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| CN2530072Y (en) * | 2001-08-31 | 2003-01-08 | 黄健 | Centrifugal pump |
| CN102338097A (en) * | 2011-10-08 | 2012-02-01 | 杭州新安江工业泵有限公司 | Centrifugal pump and adjustable manufacture method thereof |
| CN202182037U (en) * | 2011-06-23 | 2012-04-04 | 广东顺达船舶工程有限公司 | Self-absorption smashing pump |
| CN206175315U (en) * | 2016-09-27 | 2017-05-17 | 浙江工业大学 | External mixing type self -priming centrifugal pump |
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| JP2001090685A (en) * | 1999-07-22 | 2001-04-03 | Sankyo Seiki Mfg Co Ltd | Self-priming pump device |
| CN2530072Y (en) * | 2001-08-31 | 2003-01-08 | 黄健 | Centrifugal pump |
| CN202182037U (en) * | 2011-06-23 | 2012-04-04 | 广东顺达船舶工程有限公司 | Self-absorption smashing pump |
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Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
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| CN108194384A (en) * | 2017-12-21 | 2018-06-22 | 江苏双轮泵业机械制造有限公司 | A kind of centrifugal pump system |
| CN112643298A (en) * | 2020-12-25 | 2021-04-13 | 浙江燃创透平机械股份有限公司 | Flow guide pipe of gas turbine stationary blade in heat pump system and preparation method |
| GB2625470A (en) * | 2022-05-13 | 2024-06-19 | Bissell Inc | Surface cleaner |
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| CN106351881B (en) | 2019-02-01 |
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Effective date of registration: 20190517 Address after: 226400 Chaoqiao Street Industrial and Trade Road No. 8, Matang Town, Rudong County, Nantong City, Jiangsu Province Patentee after: RUDONG HUANGHAI PUMP Co.,Ltd. Address before: 056000 Xinjia Lane 207, Fuxing Road, Fuxing District, Handan City, Hebei Province Patentee before: Handan Lushan Intellectual Property Service Co.,Ltd. Effective date of registration: 20190517 Address after: 056000 Xinjia Lane 207, Fuxing Road, Fuxing District, Handan City, Hebei Province Patentee after: Handan Lushan Intellectual Property Service Co.,Ltd. Address before: 310014 Chao Wang Road, Xiacheng City, Hangzhou, Zhejiang Province, No. 18 Patentee before: Zhejiang University of Technology |