CN100392254C - Impellor used for centrifugal pump and centrifugal type fan - Google Patents
Impellor used for centrifugal pump and centrifugal type fan Download PDFInfo
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- CN100392254C CN100392254C CNB2005100323032A CN200510032303A CN100392254C CN 100392254 C CN100392254 C CN 100392254C CN B2005100323032 A CNB2005100323032 A CN B2005100323032A CN 200510032303 A CN200510032303 A CN 200510032303A CN 100392254 C CN100392254 C CN 100392254C
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- impeller
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Abstract
The present invention discloses an impeller used for a centrifugal pump and a centrifugal type fan, which comprises a wheel casing, a web plate and two or more blades arranged on the web plate. A flow channel is formed between the adjacent blades. Each blade is composed of a main blade and an auxiliary blade, wherein the main blade and the auxiliary blade are overlapped together on a minor radius end of the impeller. The distance between the main blade and the auxiliary blade is gradually widened as the radius of the impeller is increased. The main blade is connected with the auxiliary blade on the maximum radius of the impeller through a sealing plate. The present invention is the impeller used for a centrifugal pump and a centrifugal type fan, which can improve the work efficiency of the centrifugal pump and the centrifugal type fan and greatly reduce the energy consumption.
Description
Technical field
The present invention is mainly concerned with centrifugal pump and centrifugal fan field, refers in particular to a kind of impeller that is used for centrifugal pump and centrifugal fan.
Background technique
Since centrifugal pump and centrifugal blower appearance, 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 eliminate the eddy current of water in impeller 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. 1) " 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 1, 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 passage, 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.More much smaller because of impeller intake place radius again than the radius that water outlet goes out, that is to say the arc length between two blades, 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. 1) 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 the water that the centrifugal force that can only rely on minor radius water in the runner aspirates runner.Therefore this kind process takes place will influence the flow and the water inlet lift of water pump undoubtedly.
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 1) 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 1 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 water pump vane 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 water pump vane 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, again by static pressure with hydraulic pressure to outlet pipe.Again because of impeller outlet place axial width not at the spiral case center, fluid is rotated so that laterally make helical along spiral case runner one one-sided water intake, 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 lift not really high water pump and the blower fan 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 of prior art existence, the invention provides a kind of simple in structure, working efficiency that can improve centrifugal pump and centrifugal fan, the impeller that is used for centrifugal pump and centrifugal fan 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 impeller that is used for centrifugal pump and centrifugal fan, it comprises hub, web and is installed in the blade more than 2 or 2 on the web, form runner between the adjacent blades, 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.
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 the impeller that is used for centrifugal pump and centrifugal fan of the present invention is installed on centrifugal pump and centrifugal fan, 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, the impeller that is used for centrifugal pump and centrifugal fan 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 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, the impeller that is used for centrifugal pump and centrifugal fan of the present invention, because being close to, 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, the impeller that is used for centrifugal pump and centrifugal fan 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 schematic representation of blade wheel structure in the prior art;
Fig. 2 is that the master of blade wheel structure of the present invention looks schematic representation;
Fig. 3 is the cross-sectional side schematic representation of blade wheel structure of the present invention.
Marginal data
1, hub 2, web
3, blade 31, primary blades
32, back blades 4, runner
5, sealing plate
Embodiment
Below with reference to accompanying drawing the present invention is described in further details.
As shown in Figures 2 and 3, the impeller that is used for centrifugal pump and centrifugal fan of the present invention, it comprises hub 1, web 2 and is installed in the blade more than 2 or 23 on the web 2, form runner 4 between the adjacent blades 3, this blade 3 is made up of primary blades 31 and back blades 32, primary blades 31 and back blades 32 overlap one at the minor radius end of impeller, increase along with impeller radius, distance between primary blades 31 and the back blades 32 is gradually wide, and primary blades 31 links to each other by a sealing plate 5 with the maximum radius place of back blades 32 at impeller.In preferred embodiment, primary blades 31 and back blades 32 are overlapped in the thickness that together thickness equals primary blades 31 of impeller long radius end or back blades 32 in impeller minor radius end.The primary blades 31 of blade 3 and back blades 32 are formed a curved surface oblique triangle with the impeller outer diameter circular arc camber, sealing plate 5 is arranged at the place that overlaps of the primary blades 31 of blade 3 and back blades 32 and impeller outer diameter, sheet metal of sealing plate 5 usefulness is made, curved surface along impeller outer diameter is obturaged with rivet, and current are not entered in this oblique triangle district.Cavity between the primary blades 31 that this runner 4 is a blade 3 and the back blades 32 of adjacent blades 3, like this also can further make from the minor radius of impeller equal everywhere to the normal direction width of the long radius place runner 4 of impeller, the structure of whole impeller is just as be welded in circular dull and stereotyped going up with some square elbow five equilibriums, so medium flowing in impeller just become the smooth flow in the bend pipe, all approaching pressure flow field uniformly on arbitrary cross section in the runner, therefore just 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, form no eddy current, flowing of irrotational flow and no turbulence, in the whole runner except that one section of import be excessively quicken to flow, the remaining part of runner all flows near constant speed.As mentioned above, on any one cross section of runner, just no longer have the variation of malleation and negative pressure, 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.
Claims (5)
1. impeller that is used for centrifugal pump and centrifugal fan, it comprises hub (1), web (2) and be installed in the blade more than 2 or 2 (3) on the web (2), form runner (4) between the adjacent blades (3), it is characterized in that: described blade (3) is made up of primary blades (31) and back blades (32), described primary blades (31) and back blades (32) overlap one at the minor radius end of impeller, along with the increase primary blades (31) and the distance between the back blades (32) of impeller radius are gradually wide, primary blades (31) links to each other by a sealing plate (5) with the maximum radius place of back blades (32) at impeller.
2. the impeller that is used for centrifugal pump and centrifugal fan according to claim 1, it is characterized in that: described runner (4) is the cavity between the back blades (32) of the primary blades (31) of blade (3) and adjacent blades (3), and is equal everywhere to the normal direction width of the long radius place runner of impeller from the minor radius of impeller.
3. the impeller that is used for centrifugal pump and centrifugal fan according to claim 1 and 2 is characterized in that: described primary blades (31) and back blades (32) are overlapped in the thickness that together thickness equals a primary blades of impeller long radius end (31) or back blades (32) in impeller minor radius end.
4. the impeller that is used for centrifugal pump and centrifugal fan according to claim 1 and 2, it is characterized in that: the primary blades (31) of described blade (3) and back blades (32) and impeller outer diameter circular arc camber are formed a curved surface oblique triangle, and described sealing plate (5) is arranged at the place that overlaps of the primary blades (31) of blade (3) and back blades (32) and impeller outer diameter.
5. the impeller that is used for centrifugal pump and centrifugal fan according to claim 3, it is characterized in that: the primary blades (31) of described blade (3) and back blades (32) and impeller outer diameter circular arc camber are formed a curved surface oblique triangle, and described sealing plate (5) is arranged at the place that overlaps of the primary blades (31) of blade (3) and back blades (32) and impeller outer diameter.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CNB2005100323032A CN100392254C (en) | 2005-10-27 | 2005-10-27 | Impellor used for centrifugal pump and centrifugal type fan |
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CNB2005100323032A CN100392254C (en) | 2005-10-27 | 2005-10-27 | Impellor used for centrifugal pump and centrifugal type fan |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN1757932A CN1757932A (en) | 2006-04-12 |
| CN100392254C true CN100392254C (en) | 2008-06-04 |
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| CNB2005100323032A Expired - Fee Related CN100392254C (en) | 2005-10-27 | 2005-10-27 | Impellor used for centrifugal pump and centrifugal type fan |
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Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| FR3121392A1 (en) * | 2021-03-31 | 2022-10-07 | Valeo Systemes Thermiques | Ventilation device for a ventilation, heating and/or air conditioning system. |
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| CN103939391B (en) * | 2014-04-18 | 2016-05-18 | 烟台奥星电器设备有限公司 | Prop up blade and reinforce pressurizating ventilation machine |
| CN107100887A (en) * | 2017-06-30 | 2017-08-29 | 马鞍山方圆动力科技有限公司 | A kind of novel impeller |
| US10415584B2 (en) * | 2017-10-20 | 2019-09-17 | Minebea Mitsumi Inc. | Impeller and fan using the same |
| CN108953221A (en) * | 2018-07-11 | 2018-12-07 | 湖州永盛机械铸造有限公司 | A kind of centrifugal impeller |
| CN110594192B (en) * | 2018-07-17 | 2020-11-17 | 英飞同仁风机股份有限公司 | Rotor structure of centrifugal fan |
| CN210769567U (en) * | 2019-09-18 | 2020-06-16 | 中山大洋电机股份有限公司 | Draught fan |
| US11988220B2 (en) | 2019-12-17 | 2024-05-21 | Zhongshan Broad-Ocean Motor Co., Ltd. | Volute assembly and induced draft fan comprising the same |
| CN211525137U (en) * | 2019-12-17 | 2020-09-18 | 中山大洋电机股份有限公司 | Draught fan |
Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US5108257A (en) * | 1989-05-26 | 1992-04-28 | Pacific Machinery & Engineering Co., Ltd. | Impeller for turbo pump for water jet propulsion machinery, and turbo pump including same 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 |
| CN2842023Y (en) * | 2005-10-28 | 2006-11-29 | 陈瑜 | The impeller that is used for centrifugal pump and centrifugal fan |
-
2005
- 2005-10-27 CN CNB2005100323032A patent/CN100392254C/en not_active Expired - Fee Related
Patent Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US5108257A (en) * | 1989-05-26 | 1992-04-28 | Pacific Machinery & Engineering Co., Ltd. | Impeller for turbo pump for water jet propulsion machinery, and turbo pump including same 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 |
| CN2842023Y (en) * | 2005-10-28 | 2006-11-29 | 陈瑜 | The impeller that is used for centrifugal pump and centrifugal fan |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| FR3121392A1 (en) * | 2021-03-31 | 2022-10-07 | Valeo Systemes Thermiques | Ventilation device for a ventilation, heating and/or air conditioning system. |
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| CN1757932A (en) | 2006-04-12 |
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