CN206175298U - Centrifugal hydraulic turbine impeller - Google Patents
Centrifugal hydraulic turbine impeller Download PDFInfo
- Publication number
- CN206175298U CN206175298U CN201621044703.5U CN201621044703U CN206175298U CN 206175298 U CN206175298 U CN 206175298U CN 201621044703 U CN201621044703 U CN 201621044703U CN 206175298 U CN206175298 U CN 206175298U
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- Prior art keywords
- blade
- region
- impeller
- back shroud
- hydraulic turbine
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- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 claims description 11
- 238000005266 casting Methods 0.000 claims description 3
- 238000003466 welding Methods 0.000 claims description 2
- 210000000988 bone and bone Anatomy 0.000 description 6
- 239000012530 fluid Substances 0.000 description 6
- 238000010586 diagram Methods 0.000 description 5
- 239000007788 liquid Substances 0.000 description 5
- 241000237858 Gastropoda Species 0.000 description 3
- 230000008676 import Effects 0.000 description 3
- 238000000034 method Methods 0.000 description 3
- XEEYBQQBJWHFJM-UHFFFAOYSA-N Iron Chemical compound [Fe] XEEYBQQBJWHFJM-UHFFFAOYSA-N 0.000 description 2
- 230000015572 biosynthetic process Effects 0.000 description 2
- 238000005516 engineering process Methods 0.000 description 2
- 230000002093 peripheral effect Effects 0.000 description 2
- 239000000126 substance Substances 0.000 description 2
- 238000012795 verification Methods 0.000 description 2
- 229910000831 Steel Inorganic materials 0.000 description 1
- 238000005452 bending Methods 0.000 description 1
- 230000002146 bilateral effect Effects 0.000 description 1
- 238000006243 chemical reaction Methods 0.000 description 1
- 230000000295 complement effect Effects 0.000 description 1
- 230000005611 electricity Effects 0.000 description 1
- 230000029142 excretion Effects 0.000 description 1
- 229910052742 iron Inorganic materials 0.000 description 1
- 238000004519 manufacturing process Methods 0.000 description 1
- 239000003921 oil Substances 0.000 description 1
- 238000011084 recovery Methods 0.000 description 1
- 238000004064 recycling Methods 0.000 description 1
- 230000001172 regenerating effect Effects 0.000 description 1
- 238000009738 saturating Methods 0.000 description 1
- 238000000926 separation method Methods 0.000 description 1
- 230000035939 shock Effects 0.000 description 1
- 239000010959 steel Substances 0.000 description 1
- 230000008719 thickening Effects 0.000 description 1
Classifications
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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
- Y02E10/00—Energy generation through renewable energy sources
- Y02E10/20—Hydro energy
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- Structures Of Non-Positive Displacement Pumps (AREA)
Abstract
The utility model discloses a centrifugal hydraulic turbine impeller, including turbine front shroud, back shroud and blade, the blade is located between front shroud and the back shroud, and the blade is the arc, and the blade includes that root of blade is regional, blade arc region and blade tip are regional, and the blade setting is between front shroud and back shroud, and root of blade is regional clockwise on the back shroud to be placed, and blade tip is regional anticlockwise on the back shroud to be placed. The utility model has the advantages that: the efficiency of the turbine is improved, widen high-efficient district's operating range and increase the operating stability.
Description
Technical field
This utility model is related to energy conversion impeller, particularly a kind of centrifugal hydraulic turbine impeller.
Background technology
In the highly energy-consuming industry production such as iron and steel, oil, chemical industry, there are a large amount of highly pressurised liquids directly to pass through orifice plate, air relief valve
Discharge Deng device, energy is wasted.Energy regenerating hydraulic turbine can drive electrical power generators or band using liquid pressure energy
Other rotating machinery actings are moved, the recycling to liquid excess pressure energy is realized.
Centrifugal pump reversion makees turbine because having simple structure, low cost, convenient to install and maintain, and it is little to take up an area space, yield greatly,
Specification is more, adapts to head, flow and changes the economic technique superiority such as big, obtains in the industry complementary energy recovery system such as chemical industry, oil
Apply more and more widely.
Additionally, for remoteness, and but also with the area of certain hydraulics, take centrifugal pump reversion to do the side of turbine
Formula generates electricity, and has not only reduced investment outlay but also can reduce operation expense.
At present, centrifugal pump reversion makees turbine mostly using directly from the pattern of archetypal pump reversion, due to prototype impeller of pump
Pump operation operating mode is only considered during design, blade shape is backward bending type, operating turbine operating mode is not considered during the Impeller Design, this
So that efficiency is generally not higher than the efficiency of pump condition, and high efficient district narrow range during archetypal pump reversion operation.In addition, noise in operation
It is also the outstanding problem that turbine is made in pump reversion with vibration problem, governs the popularization and application that turbine technology is made in pump reversion.
Utility model content
The purpose of this utility model is the shortcoming for overcoming prior art, there is provided a kind of efficiency of turbine is high, widen high efficient district
The centrifugal hydraulic turbine impeller of range of operation and increase running stability.
The utility model discloses a kind of centrifugal hydraulic turbine impeller, including turbine front shroud, back shroud and blade, leaf
Piece is located between front shroud and back shroud, and blade is curved, and blade includes bucket root zone domain, blade arc region and blade end
Portion region, in placement clockwise on back shroud, blade tip region is on back shroud in placement counterclockwise in root of blade region.
Described blade tip region is vane inlet laying angle with the angle of the tangential direction of the circumference A of inlet side
βb1, βb1Size be 90 degree to 135 degree, inlet side be blade tip region end seamed edge.
Described root of blade region is blade exit laying angle with the angle of the tangential direction of the circumference B on outlet side
βb2, βb2Size be 0 degree to 90 degree, export side be root of blade region lateral edges.
Described blade is formed with front shroud and back shroud for an entirety and by casting or welding.
Described blade quantity is 1 to 3 times of original blade quantity in general water pump.
The protruding parts in described blade arc region are near blade tip region and positioned at 4/5ths of whole blade
Position.
This utility model has advantages below：This utility model lays angle beta by calculating optimal vane inletb1And leaf
Angle beta is laid in piece outletb2, the work efficiency of turbine blade can be effectively improved, high efficient district range of operation is widened and increases pump and makees saturating
The stationarity of overall operation during flat work, by blade protruding parts to be arranged on 4/5ths positions of blade and near leaf
Piece end regions, further increase the efficiency of turbine.
Description of the drawings
Fig. 1 is structural representation of the present utility model；
The structural representation that Fig. 2 back shrouds are connected with blade；
Fig. 3 is impeller inlet with respect to fluid flow angle and the relative fluid flow angle schematic diagram of outlet；
Fig. 4 is spiral case constant calculations schematic diagram；
Fig. 5 is that impeller inlet calculates schematic diagram with respect to fluid flow angle；
Fig. 6 is that impeller outlet laying angle calculates schematic diagram；
Test external characteristic curve figure when Fig. 7 is two different impeller operating turbines；
Fig. 8 is the flow chart of this utility model method for designing；
In figure：1- front shrouds, 2- back shrouds, 3- blades, 4- roots of blade region, 5- blade arcs region, 6- blade ends
Portion region, 7- inlet sides, 8- outlets side, 9- circumference A, 10- circumference B, 11- vane airfoil profile bone line.
Specific embodiment
This utility model is further described below in conjunction with the accompanying drawings, but protection domain of the present utility model is not limited to
Described below.
As shown in FIG. 1 to 3, the utility model discloses a kind of centrifugal hydraulic turbine impeller, including turbine front shroud
1st, back shroud 2 and blade 3, blade 3 is located between front shroud 1 and back shroud 2, and blade 3 is curved, and blade 3 includes root of blade
Region 4, blade arc region 5 and blade tip region 6, root of blade region 4 is on back shroud 2 in placement clockwise, blade
End regions 6 are on back shroud 2 in placement counterclockwise；The circle that blade tip region 6 is formed with all inlet sides 7 on back shroud 2
The angle of the tangential direction of contour A9 is that vane inlet lays angle betab1, βb1Size be 90 degree to 135 degree, inlet side 7 be blade
The end seamed edge of end regions 6；Root of blade region 4 is that blade goes out with the angle of the tangential direction of the circumference B10 on outlet side 8
Mouth lays angle betab2, βb2Size be 0 degree to 90 degree, export side 8 be root of blade region 4 lateral edges, vane inlet laying angle
βb1Angle beta is laid with blade exitb2Angular dimension arrange so that blade 3 carrying out turbine work when can reduce shock and the separation of flow
Loss, improves the efficiency for making turbine work of blade 3；Blade 3 is with front shroud 1 and back shroud 2 for an entirety and by casting
Make or weld formation.
In the present embodiment, the described quantity of blade 3 is 1 to 3 times of original blade quantity in general water pump, can be further
Improve efficiency of turbine.
In the present embodiment, the protruding parts in described blade arc region 5 are near blade tip region 6 and positioned at whole leaf
4/5ths positions of piece 3, increased blade 3 and make effective working region when turbine works, i.e., effectively widen high efficient district fortune
Line range, and increased the stationarity that pump makees overall operation when turbine works.
A kind of centrifugal hydraulic turbine method for designing impeller is comprised the following steps that：
(1) impeller of water pump is redesigned as the archetypal pump of design water pump from general water pump, archetypal pump removes impeller outer
Other specification is constant, and the design of novel impeller includes impeller inlet diameter D1, impeller outlet diameter D2, impeller inlet width b1With
The parameter of blade 3, the impeller hub diameter D of novel impellerh, impeller port ring diameter DL, impeller port ring length L, impeller it is axially overall
Length B, the front and rear cover plate overall dimensions of impeller and impeller keyway size are identical with prototype impeller, and the parameter of blade 3 includes leaf
Angle beta is laid in piece importb1Angle beta is laid with blade exitb2；
(2) suitable impeller inlet diameter D is determined to choose according to the size of archetypal pump1, impeller outlet diameter D2And impeller
Entrance width b1, it is desirable to the impeller inlet diameter D of selection1, impeller outlet diameter D2With impeller inlet width b1Can allow Novel leaf
Wheel be arranged on archetypal pump in be principle, due to the other specification of impeller it is unchanged, it is possible to determine blade 3 outlet side 7 arrive leaf
The center of piece 3 apart from R3；
(3) according to the geometric parameter of spiral case in existing archetypal pump, spiral case constant k, snail can be calculated by existing formula
Shell constantWherein Qr：Design calculated flow rate, a0：Snail shell coiling admission section centre-to-centre spacing leaf
The distance of axle centre, a0For measurable known parameters, ρ0：Snail shell coiling import circle cross section radius, ρ0For it is measurable
Know parameter,Spiral case corneriteFor measurable known parameters；
(4) energy loss due to current from volute outlet stream to impeller inlet is less, so it is considered as noenergy loss, because
The velocity moment k of the current of this impeller inlet1With the velocity moment k of volute outlet current2It is equal, and the velocity moment of volute outlet current
k2It is equal with spiral case constant, so there is k1=k2=k, so as to obtain the velocity moment k of impeller inlet current1；
(5) using the speed torque k of impeller inlet current1With impeller inlet diameter D1, water at impeller inlet can be calculated
Peripheral compoent of velocity νu1,Peripheral speed u of water at impeller inlet can be calculated using impeller rotation velocity n1,Using design calculated flow rate Qr, impeller inlet diameter D1With impeller inlet width b1, calculate water at impeller inlet
Axial plane component of velocity νm1,Wherein ψ1：Vane inlet excretion coefficient；It is relative such that it is able to calculate impeller inlet
Fluid flow angle β1,
(6) assume in design calculated flow rate QrUnder, without import is clashed into when turbo wheel works, then impeller inlet is with respect to liquid stream
Angle beta1β equal with vane inlet laying angleb1, you can determine that vane inlet lays angle betab1；
(7) it is equal due to entering the discharge of impeller inlet and the discharge of impeller outlet in the unit interval, so
Using vane inlet diameter D1Peripheral speed u of water at blade exit can be drawn2,Wherein D3：Represent blade 3
Diameter, D3=2R3；If the exit liquid flow outgoing direction of blade 3 is the lateral edges tangential direction of the termination of root of blade region 4, then may be used
Determine impeller outlet with respect to fluid flow angle β2,If the flow direction of the exit water of blade 3 exports with blade 3
Place center line of blade profile direction is consistent, then blade exit lays angle betab2Fluid flow angle β relative with impeller outlet2It is equal, i.e. βb2=β2, so as to
Obtain blade exit and lay angle betab2；
(8) vane airfoil profile bone line 11 is determined, vane airfoil profile bone line 11 lays angle beta according to vane inletb1, blade exit lay
Angle betab2Determine with subtended angle of blade, subtended angle of blade be blade import and export side place axial plane argument difference, vane inlet laying angle
βb1Angle beta is laid with blade exitb2It is referred to as blade angle, vane airfoil profile bone line 11 determines according to following two ways：First,
From vane inlet to blade exit, blade angle changes according to linear rule, subtended angle of blade self-assembling formation, vane airfoil profile bone line
11 generate naturally；Second, subtended angle of blade is given, blade angle increasingly generates the blade and blade of arc according to the principle of uniform gradual change
Aerofoil profile bone line 11；
(9) according to actual strength demand in turbine work, bulged blading thickness is determined；
(10) according to bilateral thickening principle, vane airfoil profile is generated；
(11) according to the impeller inlet diameter D for determining1, impeller outlet diameter D2, impeller inlet width b1It is straight with impeller hub
Footpath Dh, impeller port ring diameter DL, impeller port ring length L, impeller axial direction overall length B, the front and rear cover plate overall dimensions of impeller, leaf
Wheel key way size, vane inlet lay angle betab1, blade exit lay angle betab2And vane airfoil profile is generating new impeller.
In the present embodiment, described subtended angle of blade is 15 degree~90 degree.
Verification experimental verification：
In identical test platform, the new pump of archetypal pump and the hydraulic turbine impeller equipped with this utility model design is entered respectively
Row turbine is tested, and table 1 is the parameter list of impeller in archetypal pump.
Result of the test：As shown in table 2 and Fig. 7.Table 2 is that archetypal pump is contrasted with the turbine high-efficiency point of new pump, and Q is flow,
Unit is m3/h；H is lift, and unit is m；P is shaft power, and unit is kW；η is efficiency.From table 2 it can be seen that turbine is special
Peak efficiency has been brought up to 67.91% by impeller by original 59.98%, and peak efficiency absolute value improves 7.93 percentages
Point, peak efficiency improves 13.22%.Found by pressure fluctuation comparison of test results simultaneously, designed by this utility model
Impeller can significantly improve stability of the pump when operating turbine is made.
Table 1
Table 2
Fig. 7 is archetypal pump and test external characteristic curve comparison diagram during new pump operating turbine.Solid line with filled circles
The efficiency of turbine of new pump is represented, the solid line with open circles represents that efficiency during turbine is made in archetypal pump reversion, with Filled Rectangle
Solid line represent the lift of new pump operating turbine, the solid line with hollow rectangle represents that the lift of turbine is made in archetypal pump reversion,
Solid line with black triangle represents the shaft power of new pump operating turbine, and the solid line with hollow triangle represents archetypal pump
The shaft power of turbine is made in reversion.In Figure 5, from the variation tendency of efficiency curve can be seen that either low discharge to high-efficiency point
Traffic coverage, or high-efficiency point, to the range of operation of big flow, the efficiency curve that archetypal pump makees turbine is more precipitous, and new pump
The efficiency curve of turbine is flatter, particularly in 0.9~1.2 times of optimum operating condition scope, new efficiency change value 1.5% with
It is interior；In identical low discharge 70m3/ h and big flow 110m3When/h runs, the efficiency of new pump than archetypal pump efficiency high 20%,
The latter's high efficient district wider range.
Claims (6)
1. a kind of centrifugal hydraulic turbine impeller, it is characterised in that：Including turbine front shroud, back shroud and blade, blade is located at
Between front shroud and back shroud, blade is curved, and blade includes bucket root zone domain, blade arc region and blade tip area
Domain, in placement clockwise on back shroud, blade tip region is on back shroud in placement counterclockwise in root of blade region.
2. a kind of centrifugal hydraulic turbine impeller according to claim 1, it is characterised in that：Described blade tip region
The angle of the tangential direction of the circumference A formed with all inlet sides on back shroud is that vane inlet lays angle betab1, βb1Size
For 90 degree to 135 degree, inlet side is the end seamed edge in blade tip region.
3. a kind of centrifugal hydraulic turbine impeller according to claim 1, it is characterised in that：Described root of blade region
It is that blade exit lays angle beta with the angle of the tangential direction of the circumference B on outlet sideb2, βb2Size be 0 degree to 90 degree, export
Side is the lateral edges in root of blade region.
4. a kind of centrifugal hydraulic turbine impeller according to claim 1, it is characterised in that：Described blade and front shroud
Formed for an entirety and by casting or welding with back shroud.
5. a kind of centrifugal hydraulic turbine impeller according to claim 1, it is characterised in that：Described blade quantity is logical
With 1 to 3 times of original blade quantity in water pump.
6. a kind of centrifugal hydraulic turbine impeller according to claim 1, it is characterised in that：Described blade arc region
Protruding parts near blade tip region and positioned at 4/5ths positions of whole blade.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201621044703.5U CN206175298U (en) | 2016-09-09 | 2016-09-09 | Centrifugal hydraulic turbine impeller |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201621044703.5U CN206175298U (en) | 2016-09-09 | 2016-09-09 | Centrifugal hydraulic turbine impeller |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN206175298U true CN206175298U (en) | 2017-05-17 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201621044703.5U Expired - Fee Related CN206175298U (en) | 2016-09-09 | 2016-09-09 | Centrifugal hydraulic turbine impeller |
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Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN106194821A (en) * | 2016-09-09 | 2016-12-07 | 西华大学 | Centrifugal hydraulic turbine impeller and design method thereof |
| WO2021052013A1 (en) * | 2019-09-19 | 2021-03-25 | 江苏大学 | High-efficiency, low-noise automobile electronic water pump |
-
2016
- 2016-09-09 CN CN201621044703.5U patent/CN206175298U/en not_active Expired - Fee Related
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN106194821A (en) * | 2016-09-09 | 2016-12-07 | 西华大学 | Centrifugal hydraulic turbine impeller and design method thereof |
| WO2021052013A1 (en) * | 2019-09-19 | 2021-03-25 | 江苏大学 | High-efficiency, low-noise automobile electronic water pump |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| GR01 | Patent grant | ||
| GR01 | Patent grant | ||
| CF01 | Termination of patent right due to non-payment of annual fee | ||
| CF01 | Termination of patent right due to non-payment of annual fee |
Granted publication date: 20170517 Termination date: 20190909 |