CN201896785U - Double-impeller serial pump with conical hub - Google Patents
Double-impeller serial pump with conical hub Download PDFInfo
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- CN201896785U CN201896785U CN2010206714638U CN201020671463U CN201896785U CN 201896785 U CN201896785 U CN 201896785U CN 2010206714638 U CN2010206714638 U CN 2010206714638U CN 201020671463 U CN201020671463 U CN 201020671463U CN 201896785 U CN201896785 U CN 201896785U
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- impeller
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Abstract
The utility model relates to a double-impeller serial pump with a conical hub, which comprises the hub, a primary impeller, a secondary impeller and a guide vane, wherein the primary impeller, the secondary impeller and the guide vane are sequentially arranged on the hub, the guide vane is not arranged between the primary impeller and the secondary impeller, the hub is a conical hub with variable hub ratio, the primary impeller is an unadjustable impeller, and the secondary impeller is an adjustable impeller. The double-impeller serial pump is in a serial arrangement mode, so the size and the weight of a water spray propulsion system can be reduced. Because the conical hub with the variable hub ratio is adopted and loads are optimally matched on the two impellers, the energy characteristics of the water pump are improved, and the cavitation performance is improved. The double-impeller serial pump with the conical hub has the advantages of large flow, compact structure, small space size, superior energy characteristics, good anti-cavitation performance and the like.
Description
Technical field
The utility model relates to a kind of water pump, and is particularly a kind of with cone hub and put the water pump of two impellers, belongs to the hydraulic machinery field.
Background technique
Realize that high-speed small-sizeization is the trend of fluid machinery research and development always, in Aeronautics and Astronautics and water with high-tech such as water surface weapons with concern that the field of national security has irreplaceable meaning.Realize high-speed small-sizeization,, need to solve the high efficiency design problem of highly loaded blade from the fluid dynamic design aspect of fluid machinery, for being the fluid machinery of medium with liquid---for the hydraulic machinery, also to solve the cavitation problem of bringing because of high load.Use multistage form and be realize efficient and high cavitation performance finish transformation of energy method it
Present stage, the application of and have living space restriction more high-power for needs is adopted the technological scheme of twin-stage axial-flow pump usually.Conventional twin-stage axial-flow pump comprises wheel hub, first stage impeller, chopped-off head stator, secondary impeller, secondary stator as shown in Figure 1.Owing between first stage impeller and secondary impeller, be provided with the chopped-off head stator, make that the axial dimension of pump prolongs, weight increases, thereby can't satisfy the usage requirement on hydro-jet propulsion system weight and the size.Therefore, when limited space or weight were limited, the spatial arrangement of twin-stage axial-flow pump is difficulty very.
The model utility content
The purpose of this utility model is at the deficiencies in the prior art, provides a kind of and can reduce the water pump of axial dimension significantly, and improve its service behaviour.
The utility model provides a kind of bilobed wheel tandem pump with tapered wheel hub, comprise wheel hub, first stage impeller, secondary impeller, stator, different with existing bipolar axial-flow pump, first stage impeller of the present utility model, secondary impeller, stator are set in sequence on the wheel hub, between first stage impeller and secondary impeller stator are not set.Because the utility model uses the setting type of tandem, between first stage impeller and secondary impeller stator is not set, can reduce the size and the weight of hydro-jet propulsion system.
Wheel hub described in the utility model is for becoming the tapered wheel hub of hub ratio.Usually, hub ratio is determined according to specific speed.The change hub ratio design that the utility model adopts can be so that tandem lift of pump and efficient increase.
First, secondary impeller laying angle is remarkable to energy response, the influence of cavitation performance curve of tandem pump.Because the inlet incoming flow operating mode of pump is relatively stable, for simplified design, first stage impeller is designed to can not mode.Consider the influence between tandem pump first stage impeller and the secondary impeller, comparatively complicated through the mobile variation behind the first stage impeller, simultaneously in order to enlarge the efficient district of pump, secondary impeller design becomes adjustable impeller, and promptly the laying angle of blade can be regulated as required.
According to the energy principle of superposition, to ignore under the interactional situation of both stage impellers, the lift sum that tandem pump both stage impellers provides is a total head.The common head coefficient of tandem pump is very high, bears under the identical situation of equal lift and lobe numbers in both stage impellers, and the danger of first stage impeller generation cavitation is greater than secondary impeller.Need the load of impeller is carried out suitable distribution for this reason.In order to reduce the danger of first stage impeller generation cavitation, suitably reduced the load of first stage impeller during load distribution, the possibility that has reduced first stage impeller generation cavitation of so big limit.Owing to guarantee the needs of total head, when reducing first stage impeller load, will inevitably cause the increase of secondary impeller loads simultaneously.The allocation proportion relation of front and back impeller loads, still clear and definite without comparison saying.The ratio of impeller load was 4: 6 before and after the needs that impeller specific speed and blade are selected before and after considering, the utility model had been determined, promptly first stage impeller provides 40% of total head, and secondary impeller provides 60% of total head.Test result proves, no longer there are hump in flow of the present utility model and head curve, lift is monotonously change with the increase of flow, this has great importance for thrust regulation, and the efficient that the utility model produced and flow curve have almost constant efficient in very broad zone, rather than as the equally efficient district of pump very narrow.
Beneficial effect
The utility model uses the setting type of tandem, can reduce the size and the weight of hydro-jet propulsion system.Become the tapered wheel hub of hub ratio by employing, and, improved the energy response of water pump, realized the raising of cavitation performance load optimization of matching on two impellers.The utlity model has advantages such as flow is big, compact structure, bulk is little, energy response is excellent, anti-cavitation performance is good.
Description of drawings
Fig. 1 is conventional twin-stage axial-flow pump structural drawing.
Fig. 2 is a bilobed wheel tandem pump overall construction drawing;
Fig. 3 is bilobed wheel tandem pump impeller hub figure;
Fig. 4 is first stage impeller axial plane-plane figure;
Fig. 5 is the first stage impeller axonometric drawing;
Fig. 6 is secondary impeller axial plane-plane figure;
Fig. 7 is secondary impeller shaft mapping;
Fig. 8 is stator axial plane-plane figure;
Fig. 9 is the guide vane teunnion mapping.
Wherein, 1 is conventional twin-stage axial-flow pump first stage impeller, 2 is conventional twin-stage axial-flow pump chopped-off head stator, 3 is the secondary impeller of conventional twin-stage axial-flow pump, and 4 is the secondary stator of conventional twin-stage axial-flow pump, and 5 is bilobed wheel tandem pump first stage impeller, 6 is the secondary impeller of bilobed wheel tandem pump, 7 is bilobed wheel tandem pump stator, and 8 is bilobed wheel tandem pump conic diffuse, and 9 is bilobed wheel tandem pump water guide cone.
Embodiment
Below in conjunction with accompanying drawing, specify preferred implementation of the present utility model.
Fig. 2 is the overall construction drawing of realizing according to the utility model with the bilobed wheel tandem pump of tapered wheel hub, and it is made up of following five parts, and 5 is first stage impeller, and 6 is secondary impeller, and 7 is stator, and 8 is conic diffuse, and 9 is water guide cone.As can be seen from the figure, the first stage impeller number of blade is 3, secondary impeller blade number is 6, the stator number of blade is 11, and first stage impeller, secondary impeller become hub ratio.
Fig. 3 is bilobed wheel tandem pump impeller hub figure, and as can be seen from the figure impeller hub is tapered change hub ratio design.Non-adjustable, the secondary impeller laying angle of first stage impeller laying angle is adjustable.
Hub ratio is the ratio of hub diameter and impeller outer diameter, is the important structure parameter of aial flow impeller, and efficient, intensity, structure and cavitation performance are all had considerable influence.In the present embodiment, employing is the tapered wheel hub that becomes hub ratio.Usually, hub ratio is determined according to specific speed.In the present embodiment, because level impeller specific speed difference before and after the tandem pump becomes the hub ratio design so select for use.Impeller before and after having taken into account in the design by test and numerical calculation, finds that first stage impeller hub ratio scope is 0.333-0.4, and when secondary hub ratio scope was 0.4-0.467, the tandem pump can obtain best lift and efficient.
The first stage impeller of present embodiment is designed to can not mode, and secondary impeller is adjustable.Adjustable in order to realize secondary impeller, in secondary impeller, can adopt half mode (realizing the blade angle discontinuous adjustment) or full mode (the realization blade angle is regulated continuously).Full mode is to regulate oil pipe inner installation of pump shaft, arranges propeller regulating mechanism in hub body.Half mode is that blade is fixed on the hub body with nut, is carved with reference line at the root of blade, and is carved with corresponding angle line on hub body; when needs adjusting vane angle, must shut down earlier, unclamp nut then; turn to the needed angle of blade, and then fix with nut.
Fig. 4, Fig. 5 are first stage impeller axial plane-plane figure and first stage impeller axonometric drawing, and two figure have more intactly described the shape of first stage impeller.From figure, we as can be seen the first stage impeller lobe numbers be 3, hub ratio is variable, the leaf curling degree is bigger.
Fig. 6, Fig. 7 are secondary impeller axial plane-plane figure and secondary impeller shaft mapping, and two figure have more intactly described the shape of secondary impeller.From figure, our secondary as can be seen impeller blade number is 6, and hub ratio is variable.
In the present embodiment, the needs that impeller specific speed and blade are selected before and after considering, the ratio of impeller load is 4: 6 before and after having determined, and promptly first stage impeller provides 40% of total head, and secondary impeller provides 60% of total head.
Cascade solidity is the important geometric parameter of impeller, directly has influence on the efficient of pump and the quality of anti-cavitation performance.The size of blade consistency, the size of the expression blade gross area.The blade consistency reduces, and the blade gross area reduces, and friction area reduces, and can raise the efficiency; The pressure difference at the front side of vane and the back side can increase but then, and cavitation performance will be degenerated.Otherwise, increasing, energy loss will increase, and lower efficiency.Therefore cascade solidity is chosen and should be taken all factors into consideration, and makes every effort to make the minimum and cavitation performance the best of loss.What of the number of blade are closely related with cascade solidity.To set design parameter, the selection of cascade solidity should make leaf grating be operated near the optimum operating condition.For pump, cascade solidity not only influences efficient, and cavitation performance is had very big influence, also is one of deciding factor of blade strength.Lobe numbers and load distribution have substantial connection.
Impeller before and after the utility model has, should choose the number of blade respectively according to the specific speed of front and back impeller, keep constant based on blade phase angle between both stage impellers simultaneously, consider, the number of blade of secondary impeller is taken as the twice of the first stage impeller number of blade thereby reduce fluid pulse power aspect.The first stage impeller number of blade is 3 in the present embodiment like this, and secondary impeller blade number is 6.
Fig. 8, Fig. 9 are stator axial plane-plane figure and guide vane teunnion mapping, and two figure have more intactly described the shape of stator.Designed stator lobe numbers is 11 in the utility model, and the leaf curling degree is less.The main effect of stator is to eliminate from the rotatablely moving of impeller trickle, and the kinetic energy that rotatablely moves is converted into pressure energy.For axial-flow pump, its stator generally can reclaim about kinetic energy of about 10%.It should be noted that, compare with conventional twin-stage axial-flow pump, though the tandem lift of pump also is by both stage impellers stack gained, but the twin-stage axial-flow pump has had the stator of a rectification between both stage impellers, secondary impeller inlet liquid stream can be regarded nothing as and prewhirl, through after the acting of secondary impeller, flow out size and single-stage axial-flow pump basic identical of the circumferential induced velocity of secondary impeller liquid stream, be that pressure obviously increases; And bilobed wheel tandem pump is quite different, flow out the circumferential induced velocity of secondary impeller liquid stream, the circumferential induced velocity that promptly flows into stator equals the circumferential induced velocity sum that both stage impellers produces, its numerical value will be considerably beyond single-stage axial-flow pump or conventional twin-stage axial-flow pump, and in fact its effect is equal to the acting in conjunction of two stators.Because through the circumferential induced velocity vanishing of outlet after the stator rectification, therefore, the circular rector of tandem pump stator conversion is very high.
In order to dwindle the axial length of pump, often stator and diffusing tube are integrated, be called diffuser, in the utility model, as indicating 7 and 9 among Fig. 2.When determining the main structure parameters of stator, consider with the structure of blade wheel chamber and outlet pipe is unified.Adopt the cylinder type diffuser in the present embodiment, cone angle is 0.(1.4-1.5) D is got in the total length L suggestion of diffuser, thereby can make axial length less on the basis of having considered performance requirement.Get 1.47D in the present embodiment, D is the diameter of stator.Generally more than the impeller blade number, the two is prime number each other for the number of blade of stator, gets the stator number of blade 11.
Present embodiment has reduced the size and the weight of hydro-jet propulsion system greatly, and has improved the energy response of water pump, has realized the raising of cavitation performance.Present embodiment can be applied to multiple occasion, such as the marine propulsion system of amphibious vehicle, ship power, torpedo boat etc.
It should be noted last that, above embodiment is only unrestricted in order to the explanation the technical solution of the utility model, although the utility model is had been described in detail with reference to preferred embodiment, those of ordinary skill in the art is to be understood that, can make amendment or be equal to replacement the technical solution of the utility model, and not break away from the spirit and scope of technical solutions of the utility model.
Claims (10)
1. the bilobed wheel tandem pump with tapered wheel hub comprises wheel hub, first stage impeller, secondary impeller, stator, and it is characterized in that: first stage impeller, secondary impeller, stator are set in sequence on the wheel hub, between first stage impeller and secondary impeller stator are not set.
2. a kind of bilobed wheel tandem pump with tapered wheel hub according to claim 1 is characterized in that, described wheel hub is for becoming the tapered wheel hub of hub ratio.
3. a kind of bilobed wheel tandem pump with tapered wheel hub according to claim 2 is characterized in that first stage impeller hub ratio scope is 0.333-0.4, and secondary hub ratio scope is 0.4-0.467.
4. according to each described a kind of bilobed wheel tandem pump with tapered wheel hub of claim 1 to 3, it is characterized in that first stage impeller is can not the mode impeller, secondary impeller is an adjustable impeller.
5. according to each described a kind of bilobed wheel tandem pump of claim 1 to 3, it is characterized in that the load of first stage impeller is less than the load of secondary impeller with tapered wheel hub.
6. a kind of bilobed wheel tandem pump with tapered wheel hub according to claim 5 is characterized in that the ratio of first stage impeller and secondary impeller load is 4: 6.
7. a kind of bilobed wheel tandem pump with tapered wheel hub according to claim 4 is characterized in that the load of first stage impeller is less than the load of secondary impeller.
8. a kind of bilobed wheel tandem pump with tapered wheel hub according to claim 4 is characterized in that the ratio of first stage impeller and secondary impeller load is 4: 6.
9. according to each described a kind of bilobed wheel tandem pump of claim 1 to 3, it is characterized in that the number of blade of secondary impeller is taken as the twice of the first stage impeller number of blade with tapered wheel hub.
10. according to each described a kind of bilobed wheel tandem pump with tapered wheel hub of claim 1 to 3, it is characterized in that the total length of diffuser is 1.4D-1.5D, wherein D is the diameter of stator.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2010206714638U CN201896785U (en) | 2010-12-20 | 2010-12-20 | Double-impeller serial pump with conical hub |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2010206714638U CN201896785U (en) | 2010-12-20 | 2010-12-20 | Double-impeller serial pump with conical hub |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN201896785U true CN201896785U (en) | 2011-07-13 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN2010206714638U Expired - Fee Related CN201896785U (en) | 2010-12-20 | 2010-12-20 | Double-impeller serial pump with conical hub |
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| CN (1) | CN201896785U (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102003405A (en) * | 2010-12-20 | 2011-04-06 | 北京理工大学 | Double-impeller serial pump with cone-shaped hubs |
| CN111888552A (en) * | 2020-07-06 | 2020-11-06 | 河海大学 | Single-axis variable-speed two-stage asynchronous heart pump with difference iteration curve flow channel and use method |
-
2010
- 2010-12-20 CN CN2010206714638U patent/CN201896785U/en not_active Expired - Fee Related
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102003405A (en) * | 2010-12-20 | 2011-04-06 | 北京理工大学 | Double-impeller serial pump with cone-shaped hubs |
| CN102003405B (en) * | 2010-12-20 | 2012-07-11 | 北京理工大学 | Double-impeller serial pump with cone-shaped hubs |
| CN111888552A (en) * | 2020-07-06 | 2020-11-06 | 河海大学 | Single-axis variable-speed two-stage asynchronous heart pump with difference iteration curve flow channel and use method |
| CN111888552B (en) * | 2020-07-06 | 2021-05-18 | 河海大学 | Single-axis variable-speed two-stage asynchronous heart pump with difference iteration curve flow channel and use method |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| C17 | Cessation of patent right | ||
| CF01 | Termination of patent right due to non-payment of annual fee |
Granted publication date: 20110713 Termination date: 20111220 |