CN108775287A - Self priming centrifugal pump - Google Patents
Self priming centrifugal pump Download PDFInfo
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- CN108775287A CN108775287A CN201810775516.1A CN201810775516A CN108775287A CN 108775287 A CN108775287 A CN 108775287A CN 201810775516 A CN201810775516 A CN 201810775516A CN 108775287 A CN108775287 A CN 108775287A
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- 230000037452 priming Effects 0.000 title claims abstract description 86
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 claims abstract description 87
- 238000000926 separation method Methods 0.000 claims abstract description 45
- 238000007789 sealing Methods 0.000 claims abstract description 13
- 238000009434 installation Methods 0.000 claims abstract description 3
- 238000005086 pumping Methods 0.000 claims description 52
- 238000004364 calculation method Methods 0.000 claims description 13
- 230000008676 import Effects 0.000 claims description 9
- 238000010992 reflux Methods 0.000 claims description 9
- 239000003351 stiffener Substances 0.000 claims description 6
- 230000001133 acceleration Effects 0.000 claims description 4
- 230000005484 gravity Effects 0.000 claims description 4
- 230000005540 biological transmission Effects 0.000 claims description 3
- 238000009826 distribution Methods 0.000 claims description 3
- 239000000203 mixture Substances 0.000 claims description 3
- 125000004122 cyclic group Chemical group 0.000 claims description 2
- 230000001737 promoting effect Effects 0.000 abstract 1
- 239000007788 liquid Substances 0.000 description 38
- 238000010586 diagram Methods 0.000 description 11
- 239000012530 fluid Substances 0.000 description 7
- 238000009792 diffusion process Methods 0.000 description 6
- 238000002156 mixing Methods 0.000 description 6
- 238000013461 design Methods 0.000 description 5
- 238000000034 method Methods 0.000 description 5
- 230000008569 process Effects 0.000 description 5
- 230000000694 effects Effects 0.000 description 4
- 230000008859 change Effects 0.000 description 3
- 238000005516 engineering process Methods 0.000 description 3
- 230000006698 induction Effects 0.000 description 3
- 238000003860 storage Methods 0.000 description 3
- 230000003321 amplification Effects 0.000 description 2
- 238000005266 casting Methods 0.000 description 2
- 238000006243 chemical reaction Methods 0.000 description 2
- 230000008602 contraction Effects 0.000 description 2
- 230000007423 decrease Effects 0.000 description 2
- 230000003434 inspiratory effect Effects 0.000 description 2
- 230000001788 irregular Effects 0.000 description 2
- 238000003199 nucleic acid amplification method Methods 0.000 description 2
- 238000012545 processing Methods 0.000 description 2
- 230000007704 transition Effects 0.000 description 2
- 206010008469 Chest discomfort Diseases 0.000 description 1
- 241000237858 Gastropoda Species 0.000 description 1
- 241000220324 Pyrus Species 0.000 description 1
- 229910000831 Steel Inorganic materials 0.000 description 1
- 238000010276 construction Methods 0.000 description 1
- 238000007796 conventional method Methods 0.000 description 1
- 238000001816 cooling Methods 0.000 description 1
- 230000007812 deficiency Effects 0.000 description 1
- 230000005611 electricity Effects 0.000 description 1
- 230000007717 exclusion Effects 0.000 description 1
- 238000012423 maintenance Methods 0.000 description 1
- 230000007246 mechanism Effects 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 230000035772 mutation Effects 0.000 description 1
- 235000021017 pears Nutrition 0.000 description 1
- 238000004080 punching Methods 0.000 description 1
- 239000010959 steel Substances 0.000 description 1
- 230000009466 transformation Effects 0.000 description 1
- 238000009834 vaporization Methods 0.000 description 1
- 230000008016 vaporization Effects 0.000 description 1
- 238000003466 welding Methods 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
- F04D9/00—Priming; Preventing vapour lock
- F04D9/02—Self-priming 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
- F04D15/00—Control, e.g. regulation, of pumps, pumping installations or systems
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D15/00—Control, e.g. regulation, of pumps, pumping installations or systems
- F04D15/0005—Control, e.g. regulation, of pumps, pumping installations or systems by using valves
-
- 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
- F04D29/04—Shafts or bearings, or assemblies thereof
- F04D29/041—Axial thrust balancing
-
- 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
- F04D29/04—Shafts or bearings, or assemblies thereof
- F04D29/046—Bearings
-
- 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
- F04D29/08—Sealings
- F04D29/086—Sealings 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
- F04D29/18—Rotors
- F04D29/22—Rotors specially for centrifugal pumps
- F04D29/2205—Conventional flow pattern
- F04D29/2216—Shape, geometry
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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
- F04D29/18—Rotors
- F04D29/22—Rotors specially for centrifugal pumps
- F04D29/2205—Conventional flow pattern
- F04D29/2222—Construction and assembly
-
- 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
- F04D29/18—Rotors
- F04D29/22—Rotors specially for centrifugal pumps
- F04D29/2261—Rotors specially for centrifugal pumps with special measures
- F04D29/2266—Rotors specially for centrifugal pumps with special measures for sealing or thrust balance
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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
- F04D29/18—Rotors
- F04D29/22—Rotors specially for centrifugal pumps
- F04D29/24—Vanes
-
- 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
- F04D29/18—Rotors
- F04D29/22—Rotors specially for centrifugal pumps
- F04D29/24—Vanes
- F04D29/242—Geometry, shape
- F04D29/245—Geometry, shape for special effects
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Geometry (AREA)
- Structures Of Non-Positive Displacement Pumps (AREA)
Abstract
The present invention relates to a kind of self priming centrifugal pumps,Including accessory impeller hydrodynamic force sealing device,Accessory impeller hydrodynamic force sealing device includes seal base,Accessory impeller,Retainingf key,Accessory impeller spiral case,Locking nut,Trip bolt,Blade and front shroud of impeller,Outlet blade angle is 20~35 °,Subtended angle of blade is 120~160 °,The number of blade is 5~8,The gap of blade and front shroud of impeller is 0.5~1.5mm,It is 0~3 ° that runner angle of flare, which is clamped,,Seal base is fixedly connected with the supporting rack being fixed at the top of air-water separation chamber,Accessory impeller and accessory impeller spiral case are located at gas-water separation chamber interior,Accessory impeller is lockked on the driving shaft and by locking nut by retainingf key installation,Accessory impeller spiral case is located at after accessory impeller outlet and is mounted on seal base by trip bolt,Accessory impeller wasted work≤5%,Efficiency of centrifugal pump is 72%~80%.The accessory impeller work consuming of the self priming centrifugal pump of the present invention is small, efficient, there is fabulous promotional value.
Description
Technical field
The invention belongs to centrifugal pump fields, are related to a kind of self priming centrifugal pump.
Background technology
Self priming centrifugal pump is the centrifugal pump with special construction, with easy to use, reliable operation and convenient for long-range
The advantages of centralized control, (only needs the when of starting for the first time pour water, Zhi Houzhi especially suitable for sucting installation and the frequent occasion of startup
Connect startup).
Common self priming centrifugal pump is broadly divided into two kinds of structures of internal-mixing and exterior mixing, and self-suction centrifugal pump is liquid
The centrifugal pump for flowing to impeller inlet is flowed back to, whole efficiency is relatively high, and exterior mixing self-priming centrifugal pump is that liquid stream returns to impeller outlet
Centrifugal pump, whole efficiency is relatively low, but self-priming time is shorter, however either self-suction centrifugal pump or exterior mixing
Self-priming centrifugal pump, whole efficiency are all relatively low relative to general efficiency of centrifugal pump.Self priming centrifugal pump includes main impeller, accessory lobes
Wheel, reservoir chamber, pumping chamber and air-water separation chamber, pumping chamber are positioned over collection impeller outlet liquid stream energy in air-water separation chamber, often
The self priming centrifugal pump seen there are the problem of it is mainly as follows：
(1) impeller seals pressure, and the meter of sealed pressure are often only taken into account when the accessory impeller design of self priming centrifugal pump
It is usually empirical equation (only related with impeller diameter) to calculate formula, for impeller blade number, subtended angle of blade and blade exit width
Etc. parameters only rule of thumb carry out value, there is no detailed theoretical calculation method, therefore cause the wasted work of accessory impeller larger,
The accessory impeller wasted work of conventional method design is up to 10%~15%.
(2) pumping chamber of self priming centrifugal pump is usually weldment and generally rectangular cross-section section, generally use hand cut
Steel plate welds to be formed.Error hand-manipulated is big, it cannot be guaranteed that the Hydraulic Design size, to form certain hydraulic blow, waterpower
Loss is big, and rectangular cross section pumping chamber does not meet fluid flowing law, and whirlpool is easily formed in edges and corners, to form turbulent flow,
The liquid stream collected in impeller outlet can be made to be discharged to air-water separation chamber without the conversion of abundant energy in pumping chamber and carry out air water
Separation, leads to additional hydraulic loss.In addition, from impeller outlet to the liquid stream of pumping chamber import there is also impact loss and suddenly
Divergence loss, from pumping chamber be exported to air-water separation chamber during there is also unexpected divergence loss, flow stream velocity is faster, loss
It is bigger, the efficiency of pump is influenced also larger.
(3) structure and regurgitant volume of the air-water separation chamber of self priming centrifugal pump have larger impact to the performance of pump, to protect
Self-priming performance is demonstrate,proved, larger regurgitant volume can be taken when being typically designed self priming centrifugal pump, and can not achieve reflux in normal operation
The closing in hole causes pump volumetric efficiency low.Meanwhile for the self priming centrifugal pump of exterior mixing structure, return port is usually opened in snail
On shell, after pumping normal operation, air-water separation chamber flow velocity is slow, and pressure is high, and flow velocity is fast in spiral case, and pressure is low, causes liquid stream by air water
Separation chamber is flowed into pump spiral case, not only forms reflux, is also formed disturbance impact to the liquid stream in spiral case, is reduced the waterpower of pump
Efficiency and volumetric efficiency often open the self priming centrifugal pump of internal-mixing structure directly between reservoir chamber and air-water separation chamber
Hole forms reflux, and air-water separation chamber high pressure chest liquid is often caused to be flowed to reservoir chamber low pressure chamber, reduces pump volumetric efficiency.
(4) reservoir chamber of self priming centrifugal pump is usually a circular cylinder body, and liquid stream passes through import bend pipe from priming reservoir, suddenly
After diffusing to cylinder, flow stream velocity can drastically decline, and then in suction eye, flow velocity can increased dramatically again, liquid in reservoir chamber
Stream flow velocity is substantially zeroed, and after the cross-section of river meeting of liquid stream is first amplified suddenly in above process and sudden contraction, flow stream velocity are sent out
Raw mutation, and the irregular arrangement in flow direction of liquid stream, can not only influence the whole efficiency of pump, also weaken its cavitation-resistance work
With reducing the maximum suction lift of pump.
Therefore, it is great existing to develop a kind of self-priming centrifugal pump for taking into account efficiency, self-priming performance, hydraulic performance and operational reliability
Sincere justice.
Invention content
The purpose of the present invention is overcoming deficiency in the prior art, one kind is provided and takes into account efficiency, self-priming performance, hydraulic performance
With the self priming centrifugal pump of operational reliability.
In order to achieve the above object, present invention employs the following technical solutions：
Self priming centrifugal pump, including accessory impeller hydrodynamic force sealing device, accessory impeller hydrodynamic force sealing device includes accessory impeller,
Accessory impeller includes blade and impeller cover, and outlet blade angle is 20~35 °, and subtended angle of blade is 120~160 °, and the number of blade is 5~
8, the gap of blade and impeller cover is 0.5~1.5mm, and clamping runner angle of flare is 0~3 °.
As preferred technical solution：
Self priming centrifugal pump as described above, accessory impeller wasted work≤5%, the efficiency of self priming centrifugal pump is 72%~
83%, this efficiency is whole efficiency, is the product of hydraulic efficiency, volumetric efficiency and mechanical efficiency, and wherein volumetric efficiency is 87%
~95%, hydraulic efficiency is 88%~97%, and mechanical efficiency is removal accessory impeller wasted work and the friction that main impeller rotates in water
Efficiency after loss, common self priming centrifugal pump hydraulic efficiency are 78~82%, and self priming centrifugal pump of the invention is compared to existing
There is technology to significantly improve hydraulic efficiency；Self priming centrifugal pump inspiratory duration is 1~2min, and suction head is 4~8m, accessory impeller
Muzzle velocity is 15~20m/s, and it is 11~20m that accessory impeller, which exports liquid kinetic energy, and accessory impeller volute outlet flow velocity is 5~8m/s,
Accessory impeller volute outlet liquid kinetic energy is 1.5~3.5m, and pressure energy is 10~17m, it is assumed that sealed pressure 50m can be improved close
Seal pressure 20~35%.
Self priming centrifugal pump as described above, blade exit width b2The calculation formula of not tape unit be：
Kb2=2.56 (ns/100)0.99；
In formula, g is acceleration of gravity, unit m/s2, H is accessory impeller lift, and unit m, n are rotating speed, unit r/
Min, Kb2For spread factor, nsFor specific speed, Q for no sub-impeller seal when leakage rate, unit m3/ s, blade exit width
b2Unit be m；
Accessory impeller outer radius R2The calculation formula of not tape unit be：
In formula, HtFor sealed pressure, unit m, ω are angular velocity of rotation, unit rad/min, R1For accessory impeller import
Radius, unit m, accessory impeller outer radius R2Unit be m；
The calculation formula of the not tape unit of clamping flow channel length L is：
In formula, d2For runner exit equivalent diameter, unit m, d1For tunnel inlets equivalent diameter, unit m, α are diffusion
Angle, unit be °, numerical value is by nsSize determine, ns<100, angle of flare is less than 1.5 °, 100<ns<240, angle of flare is less than
2.5 °, 240<ns<320, angle of flare is less than 3.5 °, and a tan are arctan function, and the unit of clamping flow channel length L is m；
The calculation formula of the not tape unit of clamping runner number N is：
N-1=Z=9 (D2+D1)*sin[(β1+β2)/2]/(D2-D1)；
In formula, Z is the number of blade, D1And D2Respectively accessory impeller inlet diameter and outlet diameter, unit are all m, β1And β2Point
Not Wei inlet blade angle and outlet blade angle, unit is all ° that sin is SIN function, and the general runner number N that is clamped is 4~7.
Self priming centrifugal pump as described above, self priming centrifugal pump further include main impeller and the pressure water close to main impeller
Room, pumping chamber cross section are in integrally figure six, and outer ledge line is made of helix A, curve B and line C, line C while and spiral
Line A and curve B connections and intersection for pumping chamber exit face and cross section, inside edge line is circle D, spiral on outer ledge line
The center of circle E of the intersection point Y distance circles D of line A and curve B is recently and apart from the radius for being more than or equal to circle D；
There is a point X in helix A on the line segment opposite with curve B, while the flow section for crossing point X and intersection point Y will press water
Room is divided into the T1 sections of the strip being connected smoothly and T2 section cricoid, and being leaned on the helix A in T2 sections near point X has a point S,
The flow section that helix between point Y and point S intersects is coplanar with center of circle E, is class isosceles trapezoid and area gradually increases
Greatly, the flow section area for crossing S points is maximum, and the main distinction of class isosceles trapezoid and isosceles trapezoid is that side and bottom are smooth
Transition connects, and the upper bottom and bottom of class isosceles trapezoid are respectively the intersection of T2 sections of most inner sides and outermost and flow section, are owned
Class isosceles trapezoid upper bottom length it is identical.
Self priming centrifugal pump as described above, the line C are straight line, and the difference of the class isosceles trapezoid and isosceles trapezoid is also
It is smoothed curve to be to go to the bottom, and the angle of flare of T1 sections of runners is not more than 12 °；The flow section face of T1 sections of runner pumping chamber outlet ends
Product is maximum.Protection scope of the present invention is not limited to that line C is alternatively curve, and the angle of flare of T1 sections of runners is also greater than
12°。
The pumping chamber is the internal chamber of the pumping chamber pump housing；When point Y is more than the radius of circle D at a distance from the E of the center of circle, pressure
Plate in Storage reservoir pump body equipped with gap between filling intersection point Y and circle D at intersection point Y is scraped water and is forgotten, and effect is turned off water at T2 sections
Interior cycle；Surround through-hole U on the inside of T2 sections of corresponding pumping chamber pump housing sections, through-hole U mainly by coaxial cylindrical hole i and
Truncated cone-shaped through-hole j is formed by connecting and the aperture of junction through-hole i and through-hole j are equal, and through-hole i is connected to T2 sections of runners and far from logical
The hole ends j are fixed with pump cover, and pump cover is equipped with annular projection q1；
The pumping chamber pump housing is fixed on by connecting tube and stiffener plate in annular base plate, the ring inner via hole of annular base plate
Be connected to by round table-like connecting tube with through-hole U, stiffener plate circle distribution in annular base plate and simultaneously with connecting tube, cyclic annular bottom
Plate and the connection of the pumping chamber pump housing；
The main impeller is arranged in through-hole i, and the two is coaxial, and the aperture of through-hole i is the 1.01 of main impeller maximum gauge
~1.03 times, the main impeller includes preoral loop (being located at main impeller suction inlet), rear choma (being located at the main impeller back side) and connection
Screw thread, main impeller pass through from pump cover and are cased with sliding bearing, sliding bearing by connection screw thread and driving axis connection, drive shaft
Between drive shaft and pump cover, rear choma is annular projection q2, and height is more than the height of connection screw thread evagination, after main impeller
It is provided with connection preoral loop on cover board and surrounds balance hole of the space with deutostoma collar at space, annular projection q1 and annular projection q2 phases
Mutually nested and between the two equipped with wear-resistant seal ring, prosopyle loop section is inserted in connecting tube and is equipped with wear-resistant seal therebetween
Ring.
Self priming centrifugal pump as described above, self priming centrifugal pump further include air-water separation chamber and reservoir chamber, gas-water separation
Room is connected to reservoir chamber by return line, and return line is equipped with solenoid valve；Solenoid valve is passed with signal control device and pressure
Induction device is sequentially connected, and pressure sensor device is used to acquire the pressure of air-water separation chamber inner cavity, and signal control device is for receiving
The pressure signal of pressure sensor device transmission simultaneously sends current signal to solenoid valve.
Self priming centrifugal pump as described above, solenoid valve is opened when self priming centrifugal pump starts, the shut-in time of solenoid valve
It is bigger 30s~1min than the self-priming time of self priming centrifugal pump, since the pressure of self priming pump air-water separation chamber is when just beginning to ramp up
It is fluctuated due to there is the presence of gas that dynamic change is presented, it is ad hoc to put back into flow tube in order to empty the gas of air-water separation chamber
Road and solenoid valve late release, delay time, too short gas was not clean, and long power consumption is high and influences the upper water time；The letter
Number control device is signal switch board, and the pressure sensor device is pressure sensor, the signal control device be mounted on from
On support bracket outside suction centrifugal pump, signal control device support bracket is the outer independent structure of pump, determines place according to field condition
Position, the pressure sensor device are mounted in gas-water separation chamber interior walls, the signal control device and pressure sensor device
Protection domain is without being limited thereto, can also be other elements, as long as corresponding function can be realized, specific location is indefinite, can adopt
Collect the pressure of chamber in gas-water separation room；The return line positioned at solenoid valve both sides and be linked in sequence two groups mainly by returning
Flow tube, elbow and pipe fitting composition, pipe fitting is threadedly coupled with solenoid valve, two return ducts respectively with air-water separation chamber and water storage
Room is welded to connect.The connection type between air-water separation chamber and reservoir chamber is not respectively for pipe fitting and solenoid valve, two return ducts
It is limited to this, other modes that can be achieved a fixed connection are suitable for the present invention.
Self priming centrifugal pump as described above, the reservoir chamber is interior to be equipped with suction chamber, and suction chamber is hollow structure, by upper bottom
It plate, lower plate and is surrounded with the orthogonal side plate of the two, the bottom of suction chamber is provided with return port；
It is provided with hole h on upper plate and upwardly extends to form outlet pipe along hole wall, outlet pipe is connect with main impeller import, side plate
The edge line of cross section is comma shape, is linked in sequence and is formed by curve a, helix b, curve c and line d, curve a and curve c are
It smoothed curve and is seamlessly transitted between helix b, the side plate where line d is provided with hole k, and hole k is connect with water inlet pipe；Suction chamber
Shape is mainly related to the shape of side plate, and the edge line of upper plate and lower plate can be identical as the edge line of side plate cross section,
It can not also be identical；
The intersection point of helix b and curve a and curve c are respectively m and n*, and the center of circle o of m, n* and hole h are located at same straight line
On, n* is less than at a distance from m and o at a distance from o, is R with the point on helix b and the line segment length between o, on helix b
Point and o between line segment and m and o between the angle of line segment be θ, R=D0(w+v θ/r), D0For main impeller inlet diameter, w
=0.6~0.7, v=0.06~0.1, r=1 °.Curve is determined without fixed equation according to every pump discharge, lift and rotating speed
Flow section area, width and radial height can all randomly choose, and generally first take radial height, true further according to flow section area
Fixed width degree, the relationship between flow section area and pump discharge and cross-sectional flow are：
S=Q/vs；
In formula, S is flow section area, unit m2, Q is pump discharge, unit m3/ s, vsIt is single for flow section flow velocity
Position is m/s, takes (v0+v1)/2, v0For pump inlet flow velocity, v1For impeller inlet flow velocity.
For existing self-priming pump configuration without suction chamber, only reservoir chamber, structure is a circular cylinder body, liquid stream from priming reservoir pass through into
Mouth bend pipe, diffuses in cylinder, flow stream velocity drastically declines, and in suction eye, flow velocity increased dramatically again, fluid reservoir stream suddenly
Speed is substantially zeroed, is amplification suddenly in the entire waterpower cross-section of river, rear sudden contraction again, flow stream velocity vector size realizes prominent
Change process, flow direction are irregular arrangement, and this adds increased the losses of pump inlet section, not only influence pump overall operation efficiency,
Also there is abated effect to anti-cavitation performance, reduces the maximum suction lift of pump.The self priming centrifugal pump of the present invention, in reservoir chamber
Middle increase suction chamber, and after being designed as semispiral type structure, entire flow section area even variation is ensure that, to ensure to flow
The even variation of speed from small to large, flow direction also achieves even variation, effectively reduces fluid flow local diffusion and punching
Loss is hit, the way, increasing pump anti-cavitation surplus, to also further increase pump maximum suction lift, the application are improved
The maximum suction lift of self priming centrifugal pump is up to 0.5~1.0m.
Self priming centrifugal pump as described above, the suction chamber are interior equipped with the point water plate that cross section is V-arrangement, the height of point water plate
Degree is identical as suction chamber, and point water plate is connected smoothly with the side plate where helix b and the side plate where curve a respectively, liquid
Stream is roughly divided into two strands after entering suction chamber, one is along the side plate flowing where curve c and helix b, and another stock is along curve a institutes
Side plate flowing, generate impact in the side plate where helix b and side plate intersection where curve a and form whirlpool, influence
The efficiency of self priming centrifugal pump can effectively prevent liquid flow impact after point water plate is arranged, and be conducive to improve efficiency；The point water plate
Wall thickness is identical as side plate；Same wall thickness, casting cooling velocity are identical, it is not easy to casting flaw occur, weldment can reduce welding
Deformation, while also can guarantee intensity requirement；
The reservoir chamber is cylinder-like structure, is welded with suction chamber and water inlet pipe, and reservoir chamber size is set according to pump condition
Meter；The line d is camber line, and the side plate where line d is reservoir chamber side wall；The radius of curvature of the curve a is less than curve c；It is each
Position cross-sectional area is identical and is equal to the cross-sectional area of hole k；The water outlet bore is more than or equal to main impeller inlet diameter, this is
Because the flow velocity from outlet pipe to impeller inlet wants gradual and is unable to the sudden turn of events, to reduce hydraulic loss, outlet pipe slightly larger than impeller into
Mouth diameter may make outlet pipe flow velocity to be less than impeller inlet flow velocity, and the small corresponding pressure of flow velocity can be big, can reduce liquid stream vapour in this way
Change, is conducive to the anti-cavitation performance of elevator pump；The hole h and hole k is circular hole or square hole；The return port is located on lower plate,
It can also be positioned close on the side plate of lower plate, as long as being conducive to the indoor water of water storage enters suction chamber.
Self priming centrifugal pump as described above, the accessory impeller hydrodynamic force sealing device mainly by seal base, accessory impeller,
Retainingf key, accessory impeller spiral case, locking nut and trip bolt composition, seal base and the support being fixed at the top of air-water separation chamber
Frame is fixedly connected, and accessory impeller and accessory impeller spiral case are located at gas-water separation chamber interior, and accessory impeller is mounted on drive shaft by retainingf key
It above and by locking nut locks, accessory impeller spiral case is located at after accessory impeller outlet and is mounted on seal base by trip bolt
On, accessory impeller volute outlet area is calculated by centrifugal pump throat opening area, ensures sealed pressure.
Invention mechanism：
For the present invention while ensureing sub-impeller seal pressure, setting outlet blade angle is 20~35 °, accessory impeller flow
Small, pressure is high, is typical low specific speed pump, and accessory impeller outer diameter is big, and exit width is small, and efficiency is low, and the angle of outlet is arranged above-mentioned
It can guarantee that accessory lobes impeller blade can do work to liquid stream well in range, guarantee has stronger control ability, angle of outlet mistake to liquid stream
Greatly, runner diffusion can be caused serious, be unfavorable for doing work, the angle of outlet is too small, and blade passage lengthens, hardly possible processing, and along Cheng Shuili
Loss increases, and is also unfavorable for efficiency raising；It is 120~160 ° that subtended angle of blade, which is arranged, is because when outlet angular region determines, to make
Entire runner area of passage even variation, flow channel length are also limited to a range, and runner is too short to cause diffusion serious, runner
Long also to increase hydraulic loss, subtended angle of blade is that 120~160 ° of certifiable flow channel lengths meet efficiency and processing request；Setting
The number of blade is 5~8, is because after outlet blade angle and subtended angle of blade determination, the number of blade is excessive, can increase the exclusion of runner, shadow
Sealed pressure is rung, the number of blade is very few, reduces the control ability to liquid stream, and runner diffusion is serious, and efficiency reduces, outlet blade angle,
The parameter setting of subtended angle of blade and the number of blade cooperates, and influences each other；The gap of blade and impeller cover is 0.5~1.5mm,
Gap is too small to occur mechanical friction, and conference is crossed in gap influences sealing effect, and clamping runner angle of flare is 0~3 °, and runner is clamped
It must slowly be spread from liquid stream import to outlet, this is conducive to kinetic energy to pressure transformation of energy, improves hydraulic efficiency, but flow
Road angle of flare is excessive, and energy cannot be converted effectively, and whirlpool can be formed in runner, blocks runner, influences efficiency and sealed pressure.
The present invention reduces the work consuming of accessory impeller by above-mentioned parameter setting, improves the efficiency of self priming centrifugal pump.
The pumping chamber cross section of the present invention is in integrally figure six, and the flow section area of circular segment is exported along pumping chamber
Direction gradually increases, and the entire cross-section of river is pears type, and no corner angle meet fluid flowing law without vortex, reduce impeller outlet and arrive
The impact loss and divergence loss of pumping chamber import, pumping chamber liquid stream, which need to reach certain flow rate, can just enter air-water separation chamber,
Abundant conversion of the liquid flowing energy to pressure energy is realized in entire pumping chamber, and flow stream velocity can be fully converted into pressure by pumping chamber
Power can after arrange air-water separation chamber, ensure that pumping chamber flows into air-water separation chamber speed and outflow air-water separation chamber speed is equal, use up
Hydraulic loss may be reduced, self priming centrifugal pump efficiency is maximized, liquid flow path direction and air-water separation chamber cylinder is discharged in pumping chamber
Circumference is tangent, reduces impact loss and divergence loss to the greatest extent, improves the efficiency of pump.In addition, impeller outlet fluid flow angle and
It is tangent that screw type pumping chamber forgets angle so that the swiftly flowing liquid stream of impeller outlet enters pumping chamber without impact, further decreases
Hydraulic loss.
The present invention draws return line design using outer, and installs solenoid valve, and solenoid valve is passed with signal control device and pressure
Induction device is sequentially connected, and pressure sensor device acquires air-water separation chamber chamber pressure, passes to signal control device, works as pump startup
When, solenoid valve is opened, and pump reflux realizes self-priming process, is set electronic valve closing time and is more than pump self-priming time, and adds a Dingan County
Full surplus, after pumping normal operation, when the pressure of pressure sensor device acquisition reaches more than or equal to self priming centrifugal pump suction lift
Pressure needed for rated lift, signal control device receives the pressure signal that pressure sensor device is sent, and provides a 4mA electricity
Signal is flowed, this signal is passed into solenoid valve, solenoid valve is begun to shut off, and reflux course is closed, and reflux is unaffected；When pressure passes
The pressure of induction device acquisition reaches the pressure needed for rated lift less than self priming centrifugal pump suction lift, and signal control device is given
One 20mA current signal, solenoid valve start to open at, and whole process can be automatically controled reflux, to improve the way,
Self-priming performance and volumetric efficiency.
In addition, suction chamber mainly plays guiding function to impeller inlet liquid stream, liquid stream is made to enter impeller without impact, it is therefore desirable to
Liquid stream to entering impeller is dredged drainage, so that the flow velocity of liquid stream and direction cannot dash forward on each flow section
Become, because the process reduced after amplification suddenly is all with energy loss, also referred to as waterpower local losses, waterpower local losses is big,
It is low that liquid stream enters impeller pressure, and when flow stream pressure is less than pressure for vaporization, cavitation can occur for impeller, while can make pump discharge pressure
It reduces, the efficiency of pump reduces.For the problem, the present invention is provided with suction chamber in reservoir chamber and is designed to its structure, makes
Liquid stream is obtained through water inlet pipe to suction chamber, flow velocity size is held essentially constant, and reduces hydraulic loss, improves the efficiency of pump and cavitation-resistance
Energy.
Hydraulic loss calculation formula is as follows：
hs=ζ vs^2/(2g)；
In formula, hsIndicate loss pressure, unit m；ζ is loss coefficient, is constant and flow section area and speed side
Related to changing, variation is bigger, and loss coefficient is bigger；vsFor flow section flow velocity, unit m/s, g are acceleration of gravity, single
Position is m/s2, " ^ " expression square.
Found out by above formula, total hydraulic loss and loss coefficient and flow velocity are directly related, to improve the efficiency of pump, it is necessary to reduce
The value of both this.
The suction chamber outer profile busbar of the present invention is 2 sections of 360 ° of directions point, and only 180 ° use helix structure, it is assumed that leaf
Wheel inlet velocity is v0, on 180 ° of sections, flow velocity is (1/2) v for that0, suction chamber height is certain, it may be determined that 180 ° of section radial directions
Size is 0 simultaneously for 0 ° of area of section, and no liquid stream flows through, and identical in 0 ° to 180 ° each cross sectional flow rate is all (1/2) v0, lead to
The even variation of over-angle, overflow section area angularly different also uniform transitions, suction chamber height is constant, also just realizes radial
Size uniform changes.By 360 ° of impeller inlet cyclotomy circumferential direction, each angle inflow should be uniform, and liquid stream is in suction chamber along wall surface
Spiral motion, wherein there is 180 ° to use helix structure, the liquid flow flowed through on 180 ° of sections that should be evenly distributed in
On 0 °~180 ° sections, 180 ° of areas of section are set to s8, by angle bisecting be 8 parts, 22.5 ° every part, area of section s1、
s2……s8；s1=1/8s8；s2=2/8s8..., and so on；Also, this guarantees each section for the flow in each section
Surface current speed is equal, and since helix structure mean curvature radius is small, has guiding role to fluid flow, it is not easy to form flowing whirlpool
Whirlpool ensure that section liquid stream flow direction even variation, while fluid flow, so hydraulic efficiency is high, is improved without hydraulic blow
Pump whole efficiency.
Advantageous effect：
(1) self priming centrifugal pump of the invention, using full runner the Hydraulic Design, operational efficiency is high, energy-saving；
(2) self priming centrifugal pump of the invention automatically controls solenoid valve, letter by introducing return line and being equipped with
The devices such as number control device and pressure sensor device, realize the control of the reflux course between air-water separation chamber and reservoir chamber, carry
The high volumetric efficiency of pump；
(3) self priming centrifugal pump of the invention, is sealed, applied widely, sealed reliable using hydrodynamic force；
(4) self priming centrifugal pump of the invention, axial force balance and use sliding bearing limit, and pump operation is steady, reliably
Property is good；
(5) self priming centrifugal pump of the invention is equipped with wear-resistant seal ring, and pump service life is good, and maintenance cost is low；
(5) self priming centrifugal pump of the invention, by impeller outer radius to accessory impeller, clamping runner, subtended angle of blade and
The parameters such as blade exit width optimize, and reduce the work consuming of accessory impeller, improve the efficiency of pump；
(6) self priming centrifugal pump of the invention, hydraulic efficiency is high, and taking into account efficiency, self-priming performance, hydraulic performance and operation can
By property, great application prospect.
Description of the drawings
Fig. 1 is self priming centrifugal pump structural schematic diagram of the present invention；
Fig. 2 is self priming centrifugal pump accessory impeller hydrodynamic force schematic diagram of sealing device of the present invention；
Fig. 3 is self priming centrifugal pump accessory impeller front view of the present invention；
Fig. 4 is self priming centrifugal pump accessory impeller left view of the present invention；
Fig. 5 is the structural schematic diagram of self priming centrifugal pump pumping chamber of the present invention cross section；
Fig. 6 is the schematic diagram of multiple flow sections for crossing center of circle E in T2 sections in Fig. 5；(mistake in the selection of flow section such as figure
Shown in the dotted line of center of circle E) (each flow section only shows half in Fig. 6)
Fig. 7 is the schematic diagram of multiple flow sections in T1 sections in Fig. 5；
Fig. 8 is the main view sectional view of the self priming centrifugal pump pumping chamber pump housing of the present invention；
Fig. 9 is the vertical view of the self priming centrifugal pump pumping chamber pump housing of the present invention；
Figure 10 is self priming centrifugal pump blade wheel structure schematic diagram of the present invention；
Figure 11 is self priming centrifugal pump return line structural schematic diagram of the present invention；
Figure 12 is self priming centrifugal pump reservoir chamber of the present invention and suction chamber structural schematic diagram.
Figure 13 is the front view of self priming centrifugal pump reservoir chamber of the present invention and suction chamber；
Figure 14 is self priming centrifugal pump reservoir chamber of the present invention and suction chamber sectional view；
Wherein, 1- water inlet pipes, 2- reservoir chambers, 3- suction chambers, 4- outlet pipes, 5- point water plates, 6- return ducts a, 7- elbow a,
8- pipe fittings a, 9- solenoid valve, 10- pipe fittings b, 11- elbow b, 12- return duct b, 13- screw, 14- scrape water and forget, and 15- reinforces
Gusset, 16- annular base plates, the 17- pumping chamber pump housings, 18- preoral loops, 19- balance holes, choma after 20-, 21- connection screw threads, 22-
Seal base, 23- accessory impellers, 24- retainingf keys, 25- drive shafts, 26- locking nuts, 27- trip bolts, 28- accessory impeller spiral cases,
30- through-holes i, 31- through-hole j, 32- connecting tube, 33- air-water separation chambers, 34- supporting racks, 35- accessory impeller hydrodynamic force sealing devices,
36- pump covers, 37- sliding bearings, 38- return lines, 39- main impellers, 40- wear-resistant seal rings, 41- blades, 42- impeller covers.
Specific implementation mode
The invention will be further elucidated with reference to specific embodiments.It should be understood that these embodiments are merely to illustrate this hair
It is bright rather than limit the scope of the invention.In addition, it should also be understood that, after reading the content taught by the present invention, art technology
Personnel can make various changes or modifications the present invention, and such equivalent forms equally fall within the application the appended claims and limited
Fixed range.
Self priming centrifugal pump, as shown in Figure 1, including accessory impeller hydrodynamic force sealing device 35, main impeller 39, close main impeller
39 pumping chamber, air-water separation chamber 33 and reservoir chamber 2.
The accessory impeller hydrodynamic force sealing device 35 of the present invention, concrete structure is as shown in Fig. 2, mainly by seal base 22, pair
Impeller 23, retainingf key 24, accessory impeller spiral case 28, locking nut 26 and trip bolt 27 form, and seal base 22 and are fixed on gas
The supporting rack 34 at 33 top of water separation chamber is fixedly connected, and accessory impeller 23 and accessory impeller spiral case 28 are located inside air-water separation chamber 33,
Accessory impeller 23 is mounted in drive shaft 25 by retainingf key 24 and is lockked by locking nut 26, and accessory impeller spiral case 28 is located at accessory lobes
It is mounted on seal base 22 after 23 outlet of wheel and by trip bolt 27.
The concrete structure of accessory impeller 23 is as shown in Figures 3 and 4, including blade 41 and impeller cover 42, outlet blade angle 20
~35 °, subtended angle of blade is 120~160 °, and the number of blade is 5~8, and the gap of blade 41 and impeller cover 42 is 0.5~1.5mm,
It is 0~3 ° that runner angle of flare, which is clamped,.Blade exit width b2The calculation formula of not tape unit be：
Kb2=2.56 (ns/100)0.99；
In formula, g is acceleration of gravity, unit m/s2, H is accessory impeller lift, and unit m, n are rotating speed, unit r/
Min, Kb2For spread factor, nsFor specific speed, Q for no sub-impeller seal when leakage rate, unit m3/ s, blade exit width
b2Unit be m；
Accessory impeller outer radius R2The calculation formula of not tape unit be：
In formula, HtFor sealed pressure, unit m, ω are angular velocity of rotation, unit rad/min, R1For accessory impeller import
Radius, unit m, accessory impeller outer radius R2Unit be m；
The calculation formula of the not tape unit of clamping flow channel length L is：
In formula, d2For runner exit equivalent diameter, unit m, d1For tunnel inlets equivalent diameter, unit m, α are diffusion
Angle, unit are ° that a tan are arctan function, and the unit of clamping flow channel length L is m；
The calculation formula of the not tape unit of clamping runner number N is：
N-1=Z=9 (D2+D1)*sin[(β1+β2)/2]/(D2-D1)；
In formula, Z is the number of blade, D1And D2Respectively accessory impeller inlet diameter and outlet diameter, unit are all m, β1And β2Point
Not Wei inlet blade angle and outlet blade angle, unit all be °, sin is SIN function.
The pumping chamber cross section of the self priming centrifugal pump of the present invention is in integrally figure six, as shown in figure 5, outer ledge line
It is made of helix A, curve B and straight line C, straight line C connect with helix A and curve B and is pumping chamber exit face and cross simultaneously
The intersection in section, inside edge line are circle D, and the center of circle E of the intersection point Y distance circles D of helix A and curve B is most on outer ledge line
Close and distance is more than or equal to the radius of circle D.
There is a point X in helix A on the line segment opposite with curve B, while the flow section for crossing point X and intersection point Y will press water
Room is divided into the T1 sections of the strip being connected smoothly and T2 section cricoid, and the angles of flare of T1 sections of runners is not more than more in 12 °, T1 sections
The schematic diagram of a flow section near point X on helix A in T2 sections as shown in fig. 7, have a point S, between point Y and point S
Helix intersection flow section it is coplanar with center of circle E, be class isosceles trapezoid as shown in FIG. 6 and area gradually increases,
The flow section area for crossing S points is maximum, and the main distinction of class isosceles trapezoid and isosceles trapezoid is that side with bottom is smoothed
Connection is crossed, the upper bottom and bottom of class isosceles trapezoid are respectively the intersection of T2 sections of most inner sides and outermost and flow section, all
The upper bottom length of class isosceles trapezoid is identical, and it is smoothed curve that the difference of class isosceles trapezoid and isosceles trapezoid, which also resides in bottom, T1 sections
The angle of flare of runner is not more than 12 °.
Pumping chamber is the internal chamber of the pumping chamber pump housing 17, and the pumping chamber pump housing 17 is as shown in FIG. 8 and 9, and combines Fig. 1, when
When point Y is more than the radius of circle D at a distance from the E of the center of circle, between being equipped between filling intersection point Y and circle D at intersection point Y in the pumping chamber pump housing 17
The plate of gap scrapes water and forgets 14, and plate scrapes water and forgets 14 arranged direction as the tangential direction of helix A intersection point Y locations, scrapes water
14 are forgotten to be fixed on the pumping chamber pump housing 17 by screw 13；Through-hole U is surrounded on the inside of T2 sections of corresponding pumping chamber pump housing sections, is led to
Hole U is mainly formed by connecting by coaxial cylindrical hole i 30 and truncated cone-shaped through-hole j 31 and junction through-hole i 30 and through-hole j
31 aperture is equal, and through-hole i 30 is connected to T2 sections of runners and is fixed with pump cover 36 far from 31 ends through-hole j, and pump cover 36 is equipped with
Annular projection q1；The pumping chamber pump housing 17 is fixed on by connecting tube 32 and stiffener plate 15 in annular base plate 16, annular base plate 16
Ring inner via hole be connected to by round table-like connecting tube 32 with through-hole U, 15 circle distribution of stiffener plate is in annular base plate 16 and same
When connect with connecting tube 32, annular base plate 16 and the pumping chamber pump housing 17；Main impeller 39 is disposed in through-hole i 30, and the two is total
Axis, the aperture of through-hole i 30 are 1.01~1.03 times of 39 maximum gauge of main impeller.
Main impeller 39 is as shown in Figure 10, including preoral loop 18 (being located at 39 suction inlet of main impeller), rear choma 20 (are located at main lobe
Take turns 39 back sides) and connection screw thread 21, main impeller 39 is connect by connection screw thread 21 with drive shaft 25, in conjunction with shown in Fig. 1, drive shaft
25 pass through from pump cover 36 and are cased with sliding bearing 37, and sliding bearing 37 is between drive shaft 25 and pump cover 36, rear choma 20
For annular projection q2, height is more than the height of 21 evagination of connection screw thread, and connection preoral loop 18 is provided on 39 back shroud of main impeller
It surrounds space and surrounds the balance hole 19 in space with rear choma 20, annular projection q1 is mutually nested and between the two with annular projection q2
Equipped with wear-resistant seal ring 40,18 part of preoral loop is inserted in connecting tube 32 and is equipped with wear-resistant seal ring 40 therebetween.
The air-water separation chamber 33 of the self priming centrifugal pump of the present invention is connected to reservoir chamber 2 by return line 38, return duct
Road 38 is equipped with solenoid valve 9；Solenoid valve 9 is sequentially connected with signal switch board and pressure sensor, and pressure sensor is mounted on gas
On 33 inner wall of water separation chamber, the pressure for acquiring 33 inner cavity of air-water separation chamber, signal switch board is mounted on self priming centrifugal pump
On outer support bracket, for receive pressure sensor device transmission pressure signal and to solenoid valve 9 send current signal；It is self-priming
Solenoid valve 9 is opened when centrifuging pump startup, and the shut-in time of solenoid valve 9 is bigger 30s~1min than the self-priming time of self priming centrifugal pump.
38 structural schematic diagram of return line is as shown in figure 11, and return line 38 is mainly by the sequence positioned at 9 side of solenoid valve
Return duct a 6, elbow a 7 and the pipe fitting a 8 of connection, and pipe fitting b 10, elbow b 11 positioned at 9 other side of solenoid valve
It is formed with return duct b 12, pipe fitting a 8 and pipe fitting b 10 are threadedly coupled with solenoid valve 9, return duct a 6 and return duct b 12
It is welded to connect respectively with air-water separation chamber 33 and reservoir chamber 2.
Suction chamber 3 is equipped in reservoir chamber 2, structural schematic diagram is as shown in Figures 12 and 13, and reservoir chamber 2 is cylinder-like structure, is inhaled
Hydroecium 3 is hollow structure, is surrounded by upper plate, lower plate and with the orthogonal side plate of the two, the lower plate of suction chamber 3 is opened
There is return port.It is provided with hole h on upper plate and upwardly extends to form outlet pipe 4 along hole wall, outlet pipe 4 connects with 39 import of main impeller
It connects, 4 internal diameter of outlet pipe is more than or equal to impeller inlet diameter.
The edge line of side plate cross section is comma shape, as shown in figure 14, by curve a, helix b, curve c and line d sequences
Connection is formed, and curve a and curve c are smoothed curve and are seamlessly transitted between helix b that the radius of curvature of curve a is less than song
Line c, the side plate where line d are provided with hole k, and hole k is connect with water inlet pipe 1, and water inlet pipe 1 is bend pipe, and each position cross-sectional area is identical
And the cross-sectional area equal to hole k.Hole h and hole k is circular hole or square hole, and line d is camber line, and the side plate where line d is the side of reservoir chamber 2
Wall.Reservoir chamber 2 is welded with suction chamber 3 and water inlet pipe 1.
The intersection point of helix b and curve a and curve c are respectively m and n*, and the center of circle o of m, n* and hole h are located at same straight line
On, n* is less than at a distance from m and o at a distance from o, is R with the point on helix b and the line segment length between o, on helix b
Point and o between line segment and m and o between the angle of line segment be θ, R=D0(w+v θ/r), D0For 39 inlet diameter of main impeller,
W=0.6~0.7, v=0.06~0.1, r=1 °.
Equipped with the point water plate 5 that cross section is V-arrangement in suction chamber 3, the height of point water plate 5 is identical as suction chamber 3, point water plate 5
Wall thickness it is identical as side plate, point water plate 5 is connected smoothly with the side plate where helix b and the side plate where curve a respectively.
The efficiency of accessory impeller wasted work≤5% of the self priming centrifugal pump of the present invention, self priming centrifugal pump is 72%~80%,
Inspiratory duration is 1~2min, and suction head is 4~8m, and accessory impeller muzzle velocity is 15~20m/s, and it is dynamic that accessory impeller exports liquid
Can be 11~20m, accessory impeller volute outlet flow velocity is 5~8m/s, and accessory impeller volute outlet liquid kinetic energy is 1.5~3.5m, pressure
Power can be 10~17m, it is assumed that sealed pressure 20~35% can be improved in sealed pressure 50m.
Claims (10)
1. self priming centrifugal pump, including accessory impeller hydrodynamic force sealing device, accessory impeller hydrodynamic force sealing device includes accessory impeller, secondary
Impeller includes blade and impeller cover, it is characterized in that：Outlet blade angle is 20~35 °, and subtended angle of blade is 120~160 °, blade
Number is 5~8, and the gap of blade and impeller cover is 0.5~1.5mm, and clamping runner angle of flare is 0~3 °.
2. self priming centrifugal pump according to claim 1, which is characterized in that accessory impeller wasted work≤5%, it is self-priming from
The efficiency of heart pump is 72%~80%.
3. self priming centrifugal pump according to claim 2, which is characterized in that blade exit width b2Not tape unit meter
Calculating formula is：
Kb2=2.56 (ns/100)0.99；
In formula, g is acceleration of gravity, unit m/s2, H is accessory impeller lift, and unit m, n are rotating speed, unit r/min,
Kb2For spread factor, nsFor specific speed, Q for no sub-impeller seal when leakage rate, unit m3/ s, blade exit width b2's
Unit is m；
Accessory impeller outer radius R2The calculation formula of not tape unit be：
In formula, HtFor sealed pressure, unit m, ω are angular velocity of rotation, unit rad/min, R1For accessory impeller inlet radius,
Unit is m, accessory impeller outer radius R2Unit be m；
The calculation formula of the not tape unit of clamping flow channel length L is：
In formula, d2For runner exit equivalent diameter, unit m, d1For tunnel inlets equivalent diameter, unit m, α are angle of flare,
Unit is ° that a tan are arctan function, and the unit of clamping flow channel length L is m；
The calculation formula of the not tape unit of clamping runner number N is：
N-1=Z=9 (D2+D1)*sin[(β1+β2)/2]/(D2-D1)；
In formula, Z is the number of blade, D1And D2Respectively accessory impeller inlet diameter and outlet diameter, unit are all m, β1And β2Respectively
Inlet blade angle and outlet blade angle, unit all be °, sin is SIN function.
4. self priming centrifugal pump according to claim 3, which is characterized in that self priming centrifugal pump further include main impeller and
Close to the pumping chamber of main impeller, pumping chamber cross section is in integrally figure six, and outer ledge line is by helix A, curve B and line C groups
At, line C connect with helix A and curve B simultaneously and is that the intersection of pumping chamber exit face and cross section, inside edge line are circle D,
The center of circle E of the intersection point Y distance circles D of helix A and curve B is recently and apart from the radius for being more than or equal to circle D on outer ledge line；
There is a point X in helix A on the line segment opposite with curve B, while crossing the flow section of point X and intersection point Y by pumping chamber minute
For the T1 sections of the strip being connected smoothly and T2 section cricoid, being leaned on the helix A in T2 sections near point X has a point S, with point
The flow section of helix intersection between Y and point S is coplanar with center of circle E, is class isosceles trapezoid and area gradually increases, mistake
The flow section area of S points is maximum, and the main distinction of class isosceles trapezoid and isosceles trapezoid is that side with bottom is to seamlessly transit
Connection, the upper bottom and bottom of class isosceles trapezoid are respectively the intersection of T2 sections of most inner sides and outermost and flow section, all classes
The upper bottom length of isosceles trapezoid is identical.
5. self priming centrifugal pump according to claim 4, which is characterized in that the line C is straight line, the class isosceles trapezoid
It is smoothed curve that difference with isosceles trapezoid, which also resides in bottom, and the angle of flare of T1 sections of runners is not more than 12 °；
The pumping chamber is the internal chamber of the pumping chamber pump housing；When point Y is more than the radius of circle D at a distance from the E of the center of circle, pumping chamber
Plate in the pump housing equipped with gap between filling intersection point Y and circle D at intersection point Y is scraped water and is forgotten；T2 sections of corresponding pumping chamber pump housing sections
Inside surround through-hole U, through-hole U is mainly by coaxial cylindrical hole i and truncated cone-shaped through-hole j is formed by connecting and junction through-hole
The aperture of i and through-hole j are equal, and through-hole i is connected to T2 sections of runners and is fixed with pump cover far from the ends through-hole j, and pump cover is equipped with ring-type
Raised q1；
The pumping chamber pump housing is fixed on by connecting tube and stiffener plate in annular base plate, the ring inner via hole of annular base plate with it is logical
Hole U is connected to by round table-like connecting tube, stiffener plate circle distribution in annular base plate and simultaneously with connecting tube, annular base plate and
The pumping chamber pump housing connects；
The main impeller is arranged in through-hole i, and the two is coaxial, the aperture of through-hole i be main impeller maximum gauge 1.01~
1.03 times, the main impeller includes preoral loop, rear choma and connection screw thread, and main impeller is by connection screw thread and drives axis connection,
Drive shaft passes through from pump cover and is cased with sliding bearing, and for sliding bearing between drive shaft and pump cover, rear choma is cyclic annular convex
Q2 is played, height is more than the height of connection screw thread evagination, and connection preoral loop is provided on main impeller back shroud and surrounds space and deutostoma
For collar at the balance hole in space, annular projection q1 is mutually nested with annular projection q2 and is equipped with wear-resistant seal ring therebetween, preceding
Choma part is inserted in connecting tube and is equipped with wear-resistant seal ring therebetween.
6. self priming centrifugal pump according to claim 5, which is characterized in that self priming centrifugal pump further includes air-water separation chamber
And reservoir chamber, air-water separation chamber are connected to reservoir chamber by return line, return line is equipped with solenoid valve；Solenoid valve and signal
Control device and pressure sensor device are sequentially connected, and pressure sensor device is used to acquire the pressure of air-water separation chamber inner cavity, signal
Control device is used to receive the pressure signal of pressure sensor device transmission and sends current signal to solenoid valve.
7. self priming centrifugal pump according to claim 6, which is characterized in that solenoid valve is beaten when self priming centrifugal pump starts
It opens, the shut-in time of solenoid valve is bigger 30s~1min than the self-priming time of self priming centrifugal pump；The signal control device is signal
Switch board, the pressure sensor device are pressure sensor, and the signal control device is mounted on holding outside self priming centrifugal pump
On bracket, the pressure sensor device is mounted in gas-water separation chamber interior walls；The return line is mainly by being located at solenoid valve two
Side and two groups of return ducts, elbow and the pipe fitting composition being linked in sequence, pipe fitting is threadedly coupled with solenoid valve, and two return ducts divide
It is not welded to connect with air-water separation chamber and reservoir chamber.
8. self priming centrifugal pump according to claim 7, which is characterized in that be equipped with suction chamber, water suction in the reservoir chamber
Room is hollow structure, is surrounded by upper plate, lower plate and with the orthogonal side plate of the two, the bottom of suction chamber is provided with reflux
Hole；
It is provided with hole h on upper plate and upwardly extends to form outlet pipe along hole wall, outlet pipe is connect with main impeller import, and side plate is transversal
The edge line in face is comma shape, is linked in sequence and is formed by curve a, helix b, curve c and line d, curve a and curve c are smooth
It curve and is seamlessly transitted between helix b, the side plate where line d is provided with hole k, and hole k is connect with water inlet pipe；
The intersection point of helix b and curve a and curve c are respectively m and n*, and the center of circle o of m, n* and hole h are located along the same line, m with
The distance of o is less than n* at a distance from o, is R with the point on helix b and the line segment length between o, with the point and o on helix b
Between line segment and m and o between the angle of line segment be θ, R=D0(w+v θ/r), D0For main impeller inlet diameter, w=0.6~
0.7, v=0.06~0.1, r=1 °.
9. self priming centrifugal pump according to claim 8, which is characterized in that it is V-arrangement to be equipped with cross section in the suction chamber
Point water plate, the height of point water plate is identical as suction chamber, point water plate respectively with where helix b side plate and curve a where
Side plate is connected smoothly, and the wall thickness of the point water plate is identical as side plate；
The reservoir chamber is cylinder-like structure, is welded with suction chamber and water inlet pipe；The line d is camber line, the side plate where line d
For reservoir chamber side wall；The radius of curvature of the curve a is less than curve c；Its each position cross-sectional area is identical and transversal equal to hole k
Area；The water outlet bore is more than or equal to main impeller inlet diameter；The hole h and hole k is circular hole or square hole；The return port
On lower plate.
10. self priming centrifugal pump according to claim 9, which is characterized in that the accessory impeller hydrodynamic force sealing device master
To be made of seal base, accessory impeller, retainingf key, accessory impeller spiral case, locking nut and trip bolt, seal base be fixed on
Supporting rack at the top of air-water separation chamber is fixedly connected, and accessory impeller and accessory impeller spiral case are located at gas-water separation chamber interior, and accessory impeller is logical
It crosses retainingf key installation to lock on the driving shaft and by locking nut, accessory impeller spiral case is located at after accessory impeller outlet and by tight
Gu screw is mounted on seal base.
Priority Applications (1)
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Cited By (7)
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| CN111503062A (en) * | 2020-05-28 | 2020-08-07 | 李军 | Centrifugal pump with blades easy to clean |
| CN111692125A (en) * | 2019-03-12 | 2020-09-22 | 爱三工业株式会社 | Centrifugal pump |
| CN112128139A (en) * | 2020-08-13 | 2020-12-25 | 北京点域科技有限公司 | Water pump capable of changing direction of water outlet pipe |
| CN114307259A (en) * | 2021-12-30 | 2022-04-12 | 中国航空工业集团公司金城南京机电液压工程研究中心 | Pump type oil-gas separator of hydraulic combined transmission generator |
| CN114439770A (en) * | 2021-12-20 | 2022-05-06 | 陕西航天动力高科技股份有限公司 | Compact marine water cannon booster centrifugal pump |
| CN114776627A (en) * | 2022-05-14 | 2022-07-22 | 上利石集团(石家庄)泵业科技有限公司 | Self-priming pump with buffer structure |
| WO2024073943A1 (en) * | 2022-10-08 | 2024-04-11 | 利欧集团浙江泵业有限公司 | Vertical self-priming pump structure having both cavitation and hydraulic properties |
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| Publication number | Priority date | Publication date | Assignee | Title |
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| CN111692125A (en) * | 2019-03-12 | 2020-09-22 | 爱三工业株式会社 | Centrifugal pump |
| CN111503062A (en) * | 2020-05-28 | 2020-08-07 | 李军 | Centrifugal pump with blades easy to clean |
| CN112128139A (en) * | 2020-08-13 | 2020-12-25 | 北京点域科技有限公司 | Water pump capable of changing direction of water outlet pipe |
| CN114439770A (en) * | 2021-12-20 | 2022-05-06 | 陕西航天动力高科技股份有限公司 | Compact marine water cannon booster centrifugal pump |
| CN114439770B (en) * | 2021-12-20 | 2023-09-12 | 陕西航天动力高科技股份有限公司 | Compact marine water cannon booster centrifugal pump |
| CN114307259A (en) * | 2021-12-30 | 2022-04-12 | 中国航空工业集团公司金城南京机电液压工程研究中心 | Pump type oil-gas separator of hydraulic combined transmission generator |
| CN114776627A (en) * | 2022-05-14 | 2022-07-22 | 上利石集团(石家庄)泵业科技有限公司 | Self-priming pump with buffer structure |
| CN114776627B (en) * | 2022-05-14 | 2024-04-30 | 上利石集团(石家庄)泵业科技有限公司 | Self priming pump with buffer structure |
| WO2024073943A1 (en) * | 2022-10-08 | 2024-04-11 | 利欧集团浙江泵业有限公司 | Vertical self-priming pump structure having both cavitation and hydraulic properties |
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| CN108775287B (en) | 2024-03-22 |
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