CN1757931A - Centrifugal pump - Google Patents
Centrifugal pump Download PDFInfo
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- CN1757931A CN1757931A CN 200510032302 CN200510032302A CN1757931A CN 1757931 A CN1757931 A CN 1757931A CN 200510032302 CN200510032302 CN 200510032302 CN 200510032302 A CN200510032302 A CN 200510032302A CN 1757931 A CN1757931 A CN 1757931A
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- impeller
- blades
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- primary blades
- runner
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Abstract
A centrifugal pump is composed of a main body with a volute cavity at its one end, a mainshaft installed at another end of main body, and a blade wheel installed on said mainshaft and contained in said volute cavity. Said blade wheel consists of hub, webs and two or more blades installed to webs and composed of primary and secondary blades linked by a sealing plate. Its advantages are high efficiency and low energy consumption.
Description
Technical field
The present invention is mainly concerned with a kind of centrifugal pump.
Background technique
Since centrifugal pump comes out, the structure of the core component impeller of its work just is based upon on the theoretical foundation of a hypothesis always, make the blade quantity of impeller infinitely many exactly, the thickness of blade is infinitely small, thus reach eliminate water in impeller eddy current with the working efficiency that improves whole centrifugal pump to reach energy-conservation effect.But in practical structures, the blade quantity of impeller is very few, and promptly under the effective volume of centrifugal pump global design, the quantity of blade is limited, and also there is certain thickness in blade.Just because of theory this species diversity with physical presence, since how many centuries, people generally believe that the consumption of these idle works is to belong to normal.With the water pump is example, although its operational efficiency of the water pump that has less than 50%, people adhere to producing in the same old way, use in the same old way, think that this is an objective reality.True really not so, as everyone knows, the work of water pump is to rely on the high speed rotating of impeller to do work to the centrifugal force of water generates along radial direction, but water also is subjected to " Coriolis-type " power (hereinafter to be referred as coriolis force) of the another kind tangent direction opposite with the impeller rotation and the effect of inertial force simultaneously in impeller, and produces acceleration alpha
1And α
2, form the acceleration alpha of making a concerted effort.(referring to Fig. 4)." coriolis force " is necessary being, and when warp moved, its right (west) one steel rail wearing and tearing strengthened train from the arctic point of the earth; Equally, from the train that Geophysical South Pole is left, one steel rail wearing and tearing in its left side (west) strengthen, and this is because the result that " Ke Shi " power effect that the earth is produced toward rotation in the east causes.And the impeller of the impeller of shell pump and boiler induced-draft fan, referring to shown in Figure 4, its front side of vane F
1Wearing and tearing are than non-working surface F
2Want the much serious existence that also proved " Ke Shi " power.Therefore impeller is when high speed rotating, and medium suffered centrifugal force in impeller will strengthen along with the increase of radius, and " Ke Shi " power then is to strengthen with the flow velocity of water in impeller inside radius direction, and its direction is the opposite tangent direction of impeller rotation; So-called inertial force is not begin because coriolis force is a central point at water pump vane, but blade water intake radius begins, the water that is to say intake pipe did not rotate in the past at the blade passage that enters impeller, when entering blade, just begin to quicken suddenly rotation up to water, the opposite direction of this acceleration will produce inertial force, and inertial force and " coriolis force " are same direction.Impeller intake place radius is more much smaller than the radius at water outlet place, that is to say the arc length between two blades, and its outlet port is more much bigger than inlet.For a long time, people adopt the way of the axial width that dwindles impeller water outlet place to solve (referring to Fig. 4) in order to remedy the difference that this imports and exports arc length.No matter the impeller outlet axial width dwindles or does not dwindle, and all there is important disadvantages in traditional water pump vane:
1. water except that being subjected to radial centrifugal force, also is subjected to " Coriolis-type " power of tangential (laterally) and the effect of inertial force in impeller.So the working surface direction of the blade sternward that the water in close vacuum side of blade zone can be risked one's life under the effect of " Ke Shi " power and inertial force " is squeezed " and is gone.Therefore, near near the outlet port the front side of vane, water velocity will be accelerated, thereby surface friction drag is herein increased.The centrifugal force that near this moment outlet water himself is produced overcomes it inadequately and quickens the resistance that flows and brought, also will rely on the centrifugal force of the middle radius place medium of impeller that near the water the outlet " is pushed away " and go out.And the centrifugal force of its water of radius general goal is also big, should be the water that the centrifugal force of long radius place water will go to spur the minor radius place so under the normal condition, make water accelerate to enter impeller, therefore just can improve the negative pressure of water inlet, thereby improve the water inlet lift and the flow of water pump.But above phenomenon is just on the contrary.The big centrifugal force at its long radius place that also has can satisfy the surface friction drag that flows and increased near the acceleration of front side of vane one section outlet place water, but its again unable current that go to aspirate runner inlet quicken to have entered to lean on the centrifugal force of the medium and small radius water of runner to aspirate the water of runner import.Therefore the flow that this kind process will influence water pump undoubtedly takes place.
2. because the acceleration alpha that the water of close vacuum side of blade quilt " Ke Shi " power and inertial force are produced
1And α
2Gone near having pulled to another front side of vane, so will form " negative pressure " district (" F3 " zone as shown in Figure 4) near the zone the vacuum side of blade.This negative pressuren zone can draw in impeller and form eddy current with the water of the band malleation in the outer spiral casing.The water formed " water harmony " that this kind phenomenon flows down as the flow-off of mill weir causes the principle (" F4 " district as shown in Figure 4 is " water harmony " phenomenon) of eddy current.The impeller of every kind of centrifugal pump of this phenomenon (blower fan) all exists, just the degree difference.
3. the centrifugal pump impeller that also has a kind of bad structure, the axial width after the excess shrinkage of its runner exit and import equate or export slightly point.Current near front side of vane in such impeller will outwards be done accelerated motion.Can not make full use of the long radius place has big centrifugal force to aspirate the acceleration water inlet of minor radius place.Risk one's life sternward because the water of vacuum side of blade near zone is subjected to " Ke Shi " power and The Effect of Inertia Force equally that front side of vane " squeezes ", formed negative pressure and void area herein equally.But, be easy to make the water in the spiral case to enter in this negative pressure void area because impeller outlet place runner axial width is bigger.So the water that runner exit is one section can not form the pumping action to the impeller inlet place.This kind phenomenon just looks like to contain water in the basin, opens an aperture in its bottom, and the water that this moment, flowed out in the aperture is made acceleration toward dirty.The short tube that a joint internal diameter equates with the aperture if burn-on in the outlet port in hole, in-pipe flow has just become uniform motion at this moment, and the flow when comparing welded tube not is much bigger.This is because water column causes the pumping action that enters the mouth in the short tube.If 2～3 times of the enlarged diameter of institute's weldering short tube, flowing of water equally when will become with welded tube not done accelerated motion in the pipe, and its flow is the same big when also becoming with welded tube not.This is because the cause that the bottom of pipe can enter air around.Water is mobile very similar in this example and the centrifugal pump impeller runner.So should manage to avoid water not remake acceleration movement later on for one section in the impeller channel import.But runner inlet is on the contrary again, should manage to make water to have bigger acceleration to enter in the impeller channel.So it is excessive that the axial width of runner inlet should strengthen a little and descending slyness.The more important thing is and to manage to stop near the phenomenon that produces negative pressure and void area of vacuum side of blade.
4. the axial width in traditional impeller outer diameter outlet port diminishes, and export center is not or not the spiral case center, to cause following shortcoming like this, institute had kinetic energy when the former can not make full use of water and leaves impeller outer diameter, the advancing of big caliber water because how narrow water spray gets excited, so after can only changing kinetic energy into static pressure water, again by static pressure with hydraulic pressure to outlet pipe.Again because of impeller outlet place axial width not at the spiral case center, will make fluid laterally do the helical rotation along spiral case runner one is one-sided, for those small flows and high-lift pump, this kind phenomenon will especially severe, therefore consumes a lot of idle works.
From above analysis as can be known, with the lift not really high water pump bigger to those flows, more than several phenomenons less, but have influence.The more impeller of blade quantity particularly, the eddy current of vacuum side of blade negative pressure is less, but blade is overstocked, and its friction surface increases, and has also increased frictional loss.Less to those flows, the higher again water pump influence of lift will be very big, be worth that special what propose is those to be widely used in pulp pump, shell pump and all conveyings in the industrial production contain the pump that the liquid of solid matter and suspended matter stops up impeller intake easily, because of its blade quantity on the low side, the influence of above phenomenon will be bigger, so its operational efficiency also can be very low.
Summary of the invention
The technical problem to be solved in the present invention just is: at the technical problem that prior art exists, the invention provides a kind of simple in structure, working efficiency that can improve centrifugal pump, the centrifugal pump that can cut down the consumption of energy greatly.
In order to solve the problems of the technologies described above, the solution that the present invention proposes is: a kind of centrifugal pump, it comprises the pump housing, pump shaft and impeller, one end of the pump housing is cavity shape and forms spiral case, be equiped with pump shaft in the other end of the pump housing, described impeller is located in the spiral case of the pump housing and is installed on the pump shaft, described impeller comprises hub, web and be installed in the blade more than 2 or 2 on the web, form runner between the adjacent blades, water intake and the water outlet offered on the runner of described spiral case by impeller and the pump housing are communicated with, it is characterized in that: described blade is made up of primary blades and back blades, described primary blades and back blades overlap one at the minor radius end of impeller, along with the increase primary blades and the distance between the back blades of impeller radius are gradually wide, primary blades and back blades link to each other by a sealing plate at the maximum radius place of impeller.
Described runner is the cavity between the back blades of the primary blades of blade and adjacent blades, and the normal direction width from the minor radius of impeller to the long radius place runner of impeller equates everywhere.
The excircle axial width of described impeller outlet is equal to or greater than half of inner width of spiral case, and the central lines of the center line of impeller outlet and spiral case.
Described primary blades and back blades are overlapped in the thickness that together thickness equals primary blades of impeller long radius end or back blades in impeller minor radius end.
The primary blades of described blade and back blades and impeller outer diameter circular arc camber are formed a curved surface oblique triangle, and described sealing plate is arranged at the place that overlaps of the primary blades of blade and back blades and impeller outer diameter.
Compared with prior art, the invention has the advantages that:
1, after centrifugal pump impeller of the present invention is installed on centrifugal pump, can make all streamlines of the medium in the impeller channel almost all be in parallel steady flow, make this medium in each runner of impeller, not have eddy current, irrotational flow and do not have turbulence.The structure of whole impeller is just as being welded in circular dull and stereotyped going up, so medium flowing in impeller just become the smooth flow in the bend pipe with some square elbow five equilibriums.All approaching pressure flow field uniformly on arbitrary cross section in the runner.In the runner except that one section of import be excessively quicken to flow, the remaining part of runner all flows near constant speed.Therefore, on any one cross section of runner, do not have the variation of malleation and negative pressure.So eliminated the negative pressure and the hole of vacuum side of blade fully, thereby avoided the aqueous reflux in the spiral case to take place to the interior phenomenon that forms " water harmony " and eddy current of impeller;
2, centrifugal pump of the present invention is because the direction of making a concerted effort of the centrifugal force that the impeller rotation is produced and " Ke Shi " power and inertial force also almost is towards back bending direction.So the density in flow field is more even in the runner.The front said that the flow velocity in the runner was almost equal, and it is the same to flow in all right orthicon.Help the effect that the big centrifugal force at long radius place removes to aspirate current in the minor radius place runner in the impeller channel like this.Thereby the flow velocity of runner inlet water is accelerated, after the degree of vacuum in the pump water inlet improves, also just increased the flow of water pump simultaneously, thereby reach the operational efficiency that improves water pump.
3, centrifugal pump of the present invention, because being close to all, the normal direction width of each runner equates, therefore make the cross section of each runner of impeller all almost become square, wetted perimeter in the narrowed flow path of more traditional blade wheel structure is grown up and is reduced greatly, thereby strengthened the hydraulic radius in the runner, thereby reduced the hydraulic friction loss in the runner;
4, centrifugal pump of the present invention is because the more traditional width of axial width of impeller channel water outlet strengthened, so the water of outlet place ejection is no longer as traditional disconnected thin type water cake of an interblock that becomes.But become the square water column of the interruption ejection of width is greatly arranged.Thereby eliminated the eddy current of the one-sided rotary relix in the spiral case.On the other hand, because the increase of runner mouth axial width, just can make full use of the kinetic energy that runner exit place water is had when ejection, no longer the rotation because of spiral case both sides current changes part kinetic energy into potential energy, change the round transformation of energy of kinetic energy again by potential energy into, thereby also avoided some energy losses.
Description of drawings
Fig. 1 is the structural representation of centrifugal pump of the present invention;
Fig. 2 is the front elevational schematic of blade wheel structure of the present invention;
Fig. 3 is the cross-sectional side schematic representation of blade wheel structure of the present invention;
Fig. 4 is the schematic representation of blade wheel structure in the prior art.
Marginal data
1, pump shaft 2, bearing support
3, bearing 4, sealing layer
5, spiral case 6, water outlet
7, impeller 71, web
72, sealing plate 73, primary blades
74, back blades 75, runner
76, hub 77, blade
8, water intake 9, the pump housing
Embodiment
Below with reference to accompanying drawing the present invention is described in further details.
As Fig. 1, Fig. 2 and shown in Figure 3, centrifugal pump of the present invention, it comprises the pump housing 9, pump shaft 1 and impeller 7, the inside of the pump housing 9 one ends is cavity shape and forms spiral case 5, water intake 8 and the water outlet 6 offered on the runner 75 of this spiral case 5 by impeller 7 and the pump housing 9 are communicated with, and are equiped with pump shaft 1 in the other end of the pump housing 9, and this pump shaft 1 is fixed in the pump housing 9 by bearing support 2 and bearing 3, and separate with the spiral case 5 of sealing layer 4 with the other ends in itself and the pump housing 9, do not allow water flow into.Impeller 7 is located in the spiral case 5 of the pump housing 9 and is installed on the pump shaft 1, impeller 7 comprises hub 76, web 71 and is installed in the blade more than 2 or 2 77 on the web 71, form runner 75 between the adjacent blades 77, this blade 77 is made up of primary blades 73 and back blades 74, primary blades 73 and back blades 74 overlap one at the minor radius end of impeller 7, increase along with impeller 7 radiuses, distance between primary blades 73 and the back blades 74 is gradually wide, and primary blades 73 links to each other by a sealing plate 72 with the maximum radius place of back blades 74 at impeller 7.In preferred embodiment, primary blades 73 and back blades 74 are overlapped in the thickness that together thickness equals primary blades 73 of impeller 7 long radius ends or back blades 74 in impeller 7 minor radius ends.The primary blades 73 of blade 77 and back blades 74 are formed a curved surface oblique triangle with impeller 7 external diameter circular arc cambers, sealing plate 72 is arranged at the place that overlaps of the primary blades 73 of blade 77 and back blades 74 and impeller 7 external diameters, sheet metal of sealing plate 72 usefulness is made, curved surface along impeller 7 external diameters is obturaged with rivet, and current are not entered in this oblique triangle district.Cavity between the primary blades 73 that this runner 75 is a blade 77 and the back blades 74 of adjacent blades 7, like this also can further make from the minor radius of impeller 7 equal everywhere to the normal direction width of the long radius place runner 75 of impeller 7, the structure of whole impeller 7 is just as be welded in circular dull and stereotyped going up with some square elbow five equilibriums, so medium flowing in impeller 7 just become the smooth flow in the bend pipe, all approaching pressure flow field uniformly on arbitrary cross section in the runner 75, therefore just can make all streamlines of the medium in impeller 7 runners 75 almost all be in parallel steady flow, make this medium in impeller 7 each runner 75, form no eddy current, flowing of irrotational flow and no turbulence, in the whole runner 75 except that one section of import be excessively quicken to flow, the remaining part of runner 75 all flows near constant speed.As mentioned above, on runner 75 any one cross section, just no longer have the variation of malleation and negative pressure, eliminated the negative pressure and the hole at blade 77 back sides fully, thereby avoided the aqueous reflux in the spiral case 5 to take place to the impeller 7 interior phenomenons that form " water harmony " and eddy current.In preferred embodiment, can further make the excircle axial width of impeller 7 outlet be equal to or greater than half of inner width of spiral case 5, and the center line and the central lines of spiral case 5 of impeller 7 outlets, the operational efficiency to the raising pump is more favourable like this.If this spline structure, the transition zone of its water intake will have one section to stretch out the housing outside; And the runner 75 normal direction cross sections after the excess shrinkage are equated substantially with runner 75 outlet port normal direction cross sections, will eliminate the horizontal helical eddy current in the spiral case 5 after the axial width that makes impeller 7 export the water of ejection like this strengthens.Centrifugal pump of the present invention comprises all centrifugal pumps such as clean waterpump, sewage pump, slurry pump, pulp pump, chemical industry anti-corrosive pump, oil pump.
Claims (8)
1, a kind of centrifugal pump, it comprises the pump housing (9), pump shaft (1) and impeller (7), one end of the pump housing (9) is cavity shape and forms spiral case (5), be equiped with pump shaft (1) in the other end of the pump housing (9), described impeller (7) is located in the spiral case (5) of the pump housing (9) and is installed on the pump shaft (1), described impeller (7) comprises hub (76), web (71) and be installed in the blade more than 2 or 2 (77) on the web (71), form runner (75) between the adjacent blades (77), water intake (8) and the water outlet (6) offered on the runner (75) of described spiral case (5) by impeller (7) and the pump housing (9) are communicated with, it is characterized in that: described blade (77) is made up of primary blades (73) and back blades (74), described primary blades (73) and back blades (74) overlap one at the minor radius end of impeller (7), along with the increase primary blades (73) and the distance between the back blades (74) of impeller (7) radius are gradually wide, primary blades (73) links to each other by a sealing plate (72) with the maximum radius place of back blades (74) at impeller (7).
2, centrifugal pump according to claim 1, it is characterized in that: described runner (75) is the cavity between the back blades (74) of the primary blades (73) of blade (77) and adjacent blades (77), and is equal everywhere to the normal direction width of the long radius place runner (75) of impeller (7) from the minor radius of impeller (7).
3, centrifugal pump according to claim 1 and 2 is characterized in that: the excircle axial width in described impeller (7) outlet port is equal to or greater than half of inner width of spiral case (5), and the center line of impeller (7) outlet and the central lines of spiral case (5).
4, centrifugal pump according to claim 1 and 2 is characterized in that: described primary blades (73) and back blades (74) are overlapped in the thickness that together thickness equals impeller (a 7) primary blades of long radius end (73) or back blades (74) in impeller (7) minor radius end.
5, centrifugal pump according to claim 3 is characterized in that: described primary blades (73) and back blades (74) are overlapped in the thickness that together thickness equals impeller (a 7) primary blades of long radius end (73) or back blades (74) in impeller (7) minor radius end.
6, centrifugal pump according to claim 1 and 2, it is characterized in that: the primary blades (73) of described blade (77) and back blades (74) and impeller (7) external diameter circular arc camber are formed a curved surface oblique triangle, and described sealing plate (72) is arranged at the place that overlaps of the primary blades (73) of blade (77) and back blades (74) and impeller (7) external diameter.
7, centrifugal pump according to claim 4, it is characterized in that: the primary blades (73) of described blade (77) and back blades (74) and impeller (7) external diameter circular arc camber are formed a curved surface oblique triangle, and described sealing plate (72) is arranged at the place that overlaps of the primary blades (73) of blade (77) and back blades (74) and impeller (7) external diameter.
8, centrifugal pump according to claim 5, it is characterized in that: the primary blades (73) of described blade (77) and back blades (74) and impeller (7) external diameter circular arc camber are formed a curved surface oblique triangle, and described sealing plate (72) is arranged at the place that overlaps of the primary blades (73) of blade (77) and back blades (74) and impeller (7) external diameter.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CNB2005100323028A CN100392253C (en) | 2005-10-27 | 2005-10-27 | Centrifugal pump |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CNB2005100323028A CN100392253C (en) | 2005-10-27 | 2005-10-27 | Centrifugal pump |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN1757931A true CN1757931A (en) | 2006-04-12 |
| CN100392253C CN100392253C (en) | 2008-06-04 |
Family
ID=36703443
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CNB2005100323028A Expired - Fee Related CN100392253C (en) | 2005-10-27 | 2005-10-27 | Centrifugal pump |
Country Status (1)
| Country | Link |
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| CN (1) | CN100392253C (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN106678081A (en) * | 2017-01-17 | 2017-05-17 | 浙江工业大学 | Torque flow pump capable of reducing pressure pulsation |
| CN106895009A (en) * | 2017-03-30 | 2017-06-27 | 解树超 | A kind of cutting type is removed contamination one immersible pump |
Family Cites Families (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH07117076B2 (en) * | 1989-05-26 | 1995-12-18 | 太平洋機工株式会社 | Impeller for turbo pump for water jet propulsion machine and turbo pump having the impeller |
| CN2110730U (en) * | 1991-09-30 | 1992-07-22 | 石油勘探开发科学研究院机械所 | Centrifugal slurry pump |
| CN1082151C (en) * | 1998-12-22 | 2002-04-03 | 王宝利 | Self-balanced thrust blade wheel for centrifugal pump |
| JP2002138991A (en) * | 2000-11-06 | 2002-05-17 | Ebara Corp | Double suction volute pump |
| CN2842022Y (en) * | 2005-10-28 | 2006-11-29 | 陈瑜 | Centrifugal pump |
-
2005
- 2005-10-27 CN CNB2005100323028A patent/CN100392253C/en not_active Expired - Fee Related
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN106678081A (en) * | 2017-01-17 | 2017-05-17 | 浙江工业大学 | Torque flow pump capable of reducing pressure pulsation |
| CN106895009A (en) * | 2017-03-30 | 2017-06-27 | 解树超 | A kind of cutting type is removed contamination one immersible pump |
| CN106895009B (en) * | 2017-03-30 | 2023-03-14 | 解树超 | Cutting type dirt-removing integrated submersible pump |
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| Publication number | Publication date |
|---|---|
| CN100392253C (en) | 2008-06-04 |
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| C14 | Grant of patent or utility model | ||
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| EE01 | Entry into force of recordation of patent licensing contract |
Assignee: Changsha M&W Pump Manufacture (Group) Co., Ltd. Assignor: Chen Yu Contract record no.: 2011430000173 Denomination of invention: Three-baffle slide bearing centrifugal pump Granted publication date: 20080604 License type: Exclusive License Open date: 20060412 Record date: 20110913 |
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| CF01 | Termination of patent right due to non-payment of annual fee |
Granted publication date: 20080604 Termination date: 20131027 |