CN1530555A - Multistage electric pump set - Google Patents
Multistage electric pump set Download PDFInfo
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- CN1530555A CN1530555A CNA2003101134433A CN200310113443A CN1530555A CN 1530555 A CN1530555 A CN 1530555A CN A2003101134433 A CNA2003101134433 A CN A2003101134433A CN 200310113443 A CN200310113443 A CN 200310113443A CN 1530555 A CN1530555 A CN 1530555A
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- impeller
- wheel
- diffuser
- pump
- wheel hub
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- 239000012530 fluid Substances 0.000 description 26
- 238000009792 diffusion process Methods 0.000 description 5
- 230000008676 import Effects 0.000 description 4
- 239000002245 particle Substances 0.000 description 4
- 238000000034 method Methods 0.000 description 3
- 238000005452 bending Methods 0.000 description 2
- 238000010586 diagram Methods 0.000 description 2
- 230000000694 effects Effects 0.000 description 2
- 230000003628 erosive effect Effects 0.000 description 2
- 238000002474 experimental method Methods 0.000 description 2
- 230000003068 static effect Effects 0.000 description 2
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 description 2
- 230000005540 biological transmission Effects 0.000 description 1
- 238000004364 calculation method Methods 0.000 description 1
- 230000008878 coupling Effects 0.000 description 1
- 238000010168 coupling process Methods 0.000 description 1
- 238000005859 coupling reaction Methods 0.000 description 1
- 238000006073 displacement reaction Methods 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- 230000001970 hydrokinetic effect Effects 0.000 description 1
- 239000007788 liquid Substances 0.000 description 1
- 238000012067 mathematical method Methods 0.000 description 1
- 230000002093 peripheral effect Effects 0.000 description 1
- 238000000746 purification Methods 0.000 description 1
- 238000011084 recovery Methods 0.000 description 1
- 239000007787 solid Substances 0.000 description 1
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Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D1/00—Radial-flow pumps, e.g. centrifugal pumps; Helico-centrifugal pumps
- F04D1/06—Multi-stage pumps
- F04D1/063—Multi-stage pumps of the vertically split casing type
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D29/00—Details, component parts, or accessories
- F04D29/40—Casings; Connections of working fluid
- F04D29/42—Casings; Connections of working fluid for radial or helico-centrifugal pumps
- F04D29/44—Fluid-guiding means, e.g. diffusers
- F04D29/445—Fluid-guiding means, e.g. diffusers especially adapted for liquid pumps
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D29/00—Details, component parts, or accessories
- F04D29/40—Casings; Connections of working fluid
- F04D29/42—Casings; Connections of working fluid for radial or helico-centrifugal pumps
- F04D29/44—Fluid-guiding means, e.g. diffusers
- F04D29/445—Fluid-guiding means, e.g. diffusers especially adapted for liquid pumps
- F04D29/448—Fluid-guiding means, e.g. diffusers especially adapted for liquid pumps bladed diffusers
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Structures Of Non-Positive Displacement Pumps (AREA)
Abstract
A multi-stage electric pump unit, of those that consist of a multi-stage centrifugal pump with an electric motor coupled directly to the pump, where each stage consists of a pump, an impeller and a diffuser, which each have channels with vaned and vaneless zones. These zones are delimited by a shroud-surface and a hub-surface, where the b angle is the angle of the tangent at each point, characterized because, given that the Y-axis of the electric pump is the radial co-ordinate and X is the axial co-ordinate, for flow rates, Q, between 2500 and 8000 liters/minute, the points of the impeller and diffuser surface comply with the sixth degree polynomial equation, Y=f(x)=Ax6+Bx5 +Cx4+Dx3+Ex2+Fx+G, and changing the constants of the equation for each part-zone of the diffuser and impeller. Applicable to hydraulic machines.
Description
Technical field
The present invention relates to hydraulic machinery, particularly a kind of by multistage centrifugal pump and the multi-stage motor pump group formed with the direct-connected motor of pump.
Background technique
The hydraulic machinery that multi-stage motor pump group is made up of multistage centrifugal pump, its motor directly is connected with pump element.
Main hydraulic component is impeller and Diffuser.Impeller is the key element (it converts rotating speed to pressure) of every pump, though the pump housing or Diffuser are also very important, it is believed that it can enter next impeller eye from the impeller outlet changed course with fluid, thereby recovery static pressure, when the head that requires very high, each impeller serial need be arranged, thereby the multistage unit of called after water purification.
Requirement to motor-drive pump is that peak efficiency is arranged, and just can reach this requirement if impeller and Diffuser have peak efficiency.
Modern age, motor-drive pump efficient rating value was normally imported the 75%-85% of motor-drive pump total work.
Content
The purpose of this invention is to provide a kind of multi-stage motor pump group, make pump work stable, the cavitation erosion turbulent flow does not take place, and surpass motor-drive pump efficient in modern age.
The inventor expected following some be main: promptly pump work is stable, and the cavitation erosion turbulent flow does not take place, and the bending section of impeller and diffuser vane and non-bending section are directed fluid ideally, and this liquid flows the correct direction of following blade.
The applicant has developed a kind of multi-stage motor pump group, it is formed by multistage centrifugal pump with the direct-connected motor of pump, wherein the at different levels of pump form by impeller and Diffuser, their passage branch has blade sections and on-bladed section, these sections are limited in taking turns between cap surface and the hub surface, the surface each point angle of contingence is the β angle, it is a characteristic parameter, because if establish the Y-axis of motor-drive pump is y coordinate, X-axis is an abscissa, flow rate is between 2500-8000l/min, and then impeller and diffuser surface meet six following rank multinomials:
Y=f (x)=AX
6+ BX
5+ CX
4+ DX
3+ EX
2+ FX+G, for Diffuser:
A). wheel hub on-bladed district: A=B=C=D=E=0, F=0.6605, G=20.45;
B). wheel cap on-bladed district: A=B=C=D=E=0, F=0.7225, G=55.648;
C). wheel hub has vane region: A=9E-09, B=7E-06, C=-0.0019, D=0.3064, E=-26.923, F=1256.3, G=-24283;
D). wheel is stamped vane region: A=1E-10, B=-9E-08, C=2E-05, D=-0.0033, E=0.2349, F=-7.616, G=174.28;
E). wheel hub on-bladed district: A=0, B=0, C=-1E-05, D=0.0073, E=-1.7542, F=186.27, G=-7311.6;
F). wheel cap on-bladed district: A=0, B=0, C=0, D=0.0053, E=-2.6745, F=446.37 ,-G=24717;
G). wheel hub β: A=0, B=0, C=1E-06, D=-0.0002, E=0.0203, F=-1.0819, G=156.82;
H). wheel cap β: A=0, B=0, C=3E-07, D=-1E-04, E=0.0101, F=-0.7587, G=175.
Under different flow rate situations, the multinomial constant of impeller changes.
With these geometric properties of motor-drive pump element, the efficient of this motor-drive pump is far above present existing efficient, and increase reaches 14%, and this is rare in this class machinery.
In tratitional technology, impeller and Diffuser all are foundry goods, so the precision of geometrical shape/curve all can be affected, and the characteristic curve of the two is difficult to accomplish and is special.
Among the present invention, in case derive above-mentioned multinomial, machining center promptly gets and can the deviation of actual geometric configuration and theoretical shape be reduced precision programming, so the difference of practical efficiency and theoretical efficiency is very little.
Description of drawings
Purpose is for a better understanding of the present invention enclosed explanatory drawing.
Fig. 1 is that the vortex at the inlet a place of fluid f is represented.
Fig. 2 is that impeller passage wall fluid boundary layer is represented.
Fig. 3 is the expression that enters the fluid of impeller blade.
Fig. 4 is the expression of annexation between impeller and Diffuser on-bladed part, the vaneless diffuser.
Fig. 5 is the cross section and the coordinate diagram of impeller geometrical shape and runner.
Fig. 6 is the cross section and the coordinate diagram of diffuser geometrical shape and runner.
Fig. 7 is β-M% figure of wheel cap T and wheel hub C.
Embodiment
The symbol that uses is as follows:
-A ∈ [2,3,5] refers to that here A belongs to closed interval (having comprised interval end value), and this end value is 2,3 and 5.In other words, A can get any value that (comprises this 2 number) between 2,3 and 5.
-Q refers to flow rate, and its unit rises/minute (l/min).
(Z R) is the plane that defines among Fig. 5 and Fig. 6 on-plane; It is by R coordinate (y coordinate) and Z coordinate (abscissa) trace (unit of R and Z is mm).The Z axle is setovered with the Y-axis of motor-drive pump solid of rotation on plotted curve.
-wheel cap and wheel hub are expressed as curve on figure, no matter be impeller or Diffuser table body, entirely these curves are axisymmetric.
-β angle (Fig. 3 and 7).
The β angle of any is the angle (tangentially) of blade at this tangent line on the blade.
(β is M%) for the β value of each M% (therefore the percentage of the distance of passing by on the blade, be 0% in the blade starting point, is 100% at blade end) for plotted curve.
-impeller and/or diffuser passage.
This is equivalent to the wheel cap and the wheel hub of impeller and/or Diffuser, the fluid displacement that surrounds between the two adjacent blades.
-" double curvature "
This is the value from entrance edge of blade to the exit edge of blade tangential coordinates.
Given β distribution map, then (wheel cap and wheel hub) ingress " double curvature " is just set, is used for defining fully impeller passage (Diffuser too).
The composed component of impeller and Diffuser is as follows:
Wheel cap T: this is the outermost flow surface of pump flow path.
Blade: be surface with aerodynamic shape (thickness distribution with regulation) and the decision glide path that impeller, wheel hub or stator stretch out, it is the principal element that fluid is given in power transmission with regard to rotation blade.
Wheel hub C: this is the outermost flow surface of pump flow path.
The wall of the passage of impeller and/or the non-blade of Diffuser is wheel cap T and wheel hub C.
In case fluid enters impeller passage, boundary layer begins to develop on the whole blade of wheel cap and hub surface, the core that flows, at least have originally and follow the tendency that blade path flows, thereby can suppose it is even suction stream, as any distortion is arranged in suction stream, the feature of the core that then flows is just to have vortex system to exist from beginning, must be avoided.
The vortex system (see figure 1) is the example of gesture, and streamline is therein around central point revolution (promptly making nip, spout), so in fact central speed is zero, so pressure is the highest.
Contact part (V=0) with conduit wall, lower near the speed of the fluid particle of this wall, form the fluid layer that one deck is called boundary layer, fluid particle speed is less than the speed that is not subjected to the disturbance zone in this layer.
U
Boundary layer＜U
Other particles
In the formula: U is the overall rate of particle.
δ is defined as the thickness (see figure 2) of boundary layer cp, and this is 99% the each point geometric position that its speed approximates boundary layer outside speed.
Under the situation that fluid flows in impeller passage, fluid core portion C F and boundary layer seam are subjected to complicated strength, form complicated flow model.Originally boundary layer follows the free stream direction, but boundary layer and fluid core partly are subjected to the influence of whole passage strength under the situation that fluid flows in impeller passage, Just because of this, secondary flow partly takes place at fluid core, it and forms flowing of high momentum at the wheel hub press area near the wheel cap suction surface.
Usually, it is main flowing that secondary flow is considered to viscous effect, otherwise once to be considered to dynamic effect be main flowing to stream.
Total characteristic is to determine that once stream and secondary flow are all observed conservation equation (this equation and boundary conditions determine fluid to be in turn state or invariant state when moving by conduit together)
The basic hydrokinetics feature of pump stage can use that following principle studies each parts in great detail and the base speed triangle is done introduction, and these principles are:
1) first principle is the principle of mass conservation.
2) newton's equation of motion of angular coordinates system.
3) Europe of turbomachinery control equation, this equation brief description increment equals the variation of moment of momentum.Use these principles and can study the velocity triangle of flow each point.
Most important point is the inlet 1 between the blade (2) of impeller, and major parameter is shown in Fig. 3.
Find out that thus the same fluid that enters the mouth with radial velocity Cm intake impeller can have multiple import fluidised form.
As seen fluid moves from peripheral velocity U=2. π .r.N with pump wheel.According to following basic principle render speed triangle.
Relative velocity+impeller speed=absolute velocity
For the impeller suction stream, the situation of Co=0 (fluid is with the perfect condition intake impeller), flow angle determines that by inlet radial velocity (by mass flow rate and density Variable Control) and the local speed U of impeller gained relative current angle is β relatively.
If β equals blade angle, then fluid is accurately followed direction blade and is flowed, but under different situations, this angle may be greater than or less than blade angle, therefore, flowing has certain angle of attack, when any prewhirling (water rotates before advancing impeller) no matter with motor shaft be with turning to or counter steer, the inlet fluidised form also has very big change.
Can obtain desirable impeller eye with appropriate import design.
By not only changing mass flow rate but also change flow area, relative velocity W1t (relative velocity of 1 pair of wheel cap of impeller inlet) minimum, when gathering way because of inlet diameter or circulation area when increasing, U increases, if flow area dwindles, mean the increase of mass area ratio flow and Cm.
Radial velocity component Cm is determined that by mass-conservation equation definitely flowing the angle is the result of calculation of relative current angle and impeller speed, in fact, flow angle is not strict presses blade in outlet, and certain difference is arranged, from the tangential velocity viewpoint, this difference is called Sliding velocity, can derive sliding ratio thus.
For radially blade and bent leaf, synthetic absolute flow angle α is very big: representative value is α=50 °-80 ° (radial coordinate) or α '=10 °-40 ° (tangential coordinates).Modal angular dimension is: α '=15 °-25 ° and α=65 °-75 °.Discharge velocity triangle is important, because not only can determine merit value or pressure to increase, and can understand pressure surge and changes with mass flow rate.
In case operating conditions regulation and impeller adiabatic efficiency are known, then except also calculating the flow of import to outlet the fine estimation slip ratio, the feature of resulting flow is that outlet has a large amount of kinetic energy and certain curl.
Efficient connects isentropic work (isentropic work=can be used to reach the minimum work of requirement head) and actual work as previously mentioned, and this is thermodynamic (al) strict difinition.
In order to determine velocity triangle, must know the efficient of impeller, but accomplish that this point is remarkable.
What next step will be considered is vaneless diffuser, i.e. the rate of discharge of vaneless diffuser any point.
According to law of conservation of angular momentum, the radius of changing into the route of mean flowrate description can be transformed into kinetic energy the static pressure increment.
What moment of momentum was said is the impeller output terminal moment of momentum consistent with law of conservation of angular momentum.In fact, the segment angle momentum has disappeared when flow moves by the on-bladed diffuser, therefore must do accurately to calculate to estimate this loss, we can say about the moment of momentum possible loss 5%-15% of expection.
The radial component Cm of overall rate can by mass-conservation equation (density than known situation under) accurately mark, otherwise flow angle can combine this two relation definite, the flow angle by the on-bladed diffuser depends on channel width.
The flow area that must observe in the diffuser changes as kinetic energy and is transformed into the second method that pressure can increase.
Diffuser is also playing an important role aspect adjusting flow and the control radial thrust as the tie point between the different parts.
On-bladed diffuser 3 (see figure 4)s mainly are made up of two parallel wall 4, form the annular radial passage of an opening, rise to certain boundary of effective long radius from impeller outlet 5, sometimes its back is a voluted type trap, other situation back is a diffuser housing, but some Diffuser does not have " recess ", under other situation, increase the useless on-bladed diffuser of occasion at area, this is the part as the input system of inlet passage formula diffusion structure.
Between impeller and the diffusion housing (blade is arranged) the on-bladed diffuser is arranged, help to prevent the coupling of vibrations wave mode between the blade of diffusion housing and Diffuser like this, thereby prevent that diffusion housing entrance edge of blade is stressed and lost efficacy because of tired.
Also can be applicable to the diffusion housing of following continuously behind the impeller, its blade is right after impeller outlet and extends to the next stage import.
Consider everything adjusting factor, the applicant has finished the experiment of mass efficient, and calculates with the method for computational fluid mechanics CFD, optimum shape is obtained in circulation each point pointwise in the pump, so that reach optimum efficiency.
This geometrical shape is being illustrated on the coordinate axes, wherein the Y-axis of pump is that y coordinate (Y ≡ R) and X ≡ Z are the radial coordinates on the abscissa Y, and application of mathematical method is derived a simple equation to this geometrical shape, it meets margin of error ± 3.5% with the laboratory data that obtains.
This equation is multinomial Y=AX
6+ BX
5+ CX
4+ DX
3+ EX
2+ FX+G, constant A in the formula, B, C, D, E, F and G must seek at respectively the distinguishing of pump that fluid flows through.
Fig. 5 is the flow chart and the geometrical shape of impeller, and rachis is by on-bladed district 6 (fluid from inlet enters this district) and have vane region 7 (direction of flow Diffuser wherein) to form.Two end faces of visible wheel cap T and wheel hub C among the figure.
Fig. 6 is the flow chart and the geometrical shape of housing or Diffuser, and Diffuser comprises initial on-bladed district 8 (fluid enters wherein from impeller outlet) in this example, and the vane region 9 and the second on-bladed district 10 are arranged, and fluid is changed direction enter the next stage impeller.
The scope of having made the flow rate Q that studies be the 2500-8000 liter/minute.
In completed experiment, the applicant thinks, in order to reach optimum efficiency, the critical piece of motor-drive pump is a pump housing diffuser, so it remains unchanged, and feasible when the scope of flow rate Q changes be to revise impeller, for this reason, first kind of impeller of described multinomial is suitable for flow rate Q
1And scope be the 2500-6000 liter/minute, second kind of impeller is suitable for flow rate Q
2Scope be the 4500-8000 liter/minute.
This formula is: Y=f (x)=AX
6+ BX
5+ CX
4+ DX
3+ EX
2+ FX+G
| Symbol | ?A | ?B | ?C | ?D | ?E | ?F | ?G | Interval |
| Q 1/I/NA/C | ?0 | ?0 | ?0 | ?6E-05 | ?0.0014 | ?-0.0146 | ?27.511 | [1，40.5] |
| Q 1/I/NA/T | ?0 | ?0 | ?0 | ?0 | ?0 | ?0 | ?64.5 | [1，9] |
| Q 1/I/A/C | ?0 | ?0 | ?5E-06 | ?-0.0014 | ?0.1535 | ?-6.3821 | ?121.24 | [40.5，83] |
| Q 1/I/A/T | ?-4E-08 | ?8E-06 | ?-0.0006 | ?0.0247 | ?-04771 | ?4.3023 | ?50.015 | [9，54.09] |
| Q 1/I/β/C | ?0 | ?3E-09 | ?-9E-07 | ?0.0001 | ?-0.0042 | ?-0.0915 | ?34.402 | [0，100] |
| Q 1/I/β/T | ?0 | ?1E-09 | ?-5E-07 | ?6E-05 | ?-0.0044 | ?0.1822 | ?22.2 | [0，100] |
| Q 1?y?Q 2/D/NA/C | ?0 | ?0 | ?0 | ?0 | ?0 | ?0.6605 | ?20.45 | [83，88] |
| Q 1?y?Q 2/D/NA/T | ?0 | ?0 | ?0 | ?0 | ?0 | ?0.7225 | ?55.648 | [54.09，60] |
| Q 1?y?Q 2/D/A/C | ?-9E-09 | ?7E-06 | ?-0.0019 | ?0.3064 | ?-26.923 | ?1256.3 | ?-24283 | [88，154] |
| Q 1?y?Q 2/D/A/T | ?1E-10 | ?-9E-08 | ?2E-05 | ?-0.0033 | ?0.2349 | ?-7.616 | ?174.28 | [60，163.5] |
| Q 1?y?Q 2/D/NA/C | ?0 | ?0 | ?-1E-05 | ?0.0073 | ?-1.7542 | ?186.27 | ?-7311.6 | [154，174] |
| Q 1?y?Q 2/D/NA/T | ?0 | ?0 | ?0 | ?0.0053 | ?-2.6745 | ?446.37 | ?-24717 | [163.5，174] |
| Q 1?y?Q 2/D/β/C | ?0 | ?0 | ?1E-06 | ?-0.0002 | ?0.0203 | ?-1.0819 | ?156.82 | [0，100] |
| Q 1?y?Q 2/D/β/T | ?0 | ?0 | ?3E-07 | ?-1E-04 | ?0.0101 | ?-0.7587 | ?175 | [0，100] |
| Q 2/L/NA/C | ?0 | ?0 | ?0 | ?5E-05 | ?0.0013 | ?-0.0139 | ?27.511 | [1，41] |
| Q 2/I/NA/T | ?0 | ?0 | ?0 | ?0 | ?0 | ?0 | ?64.5 | [1，7] |
| Q 2/I/A/C | ?0 | ?0 | ?5E-06 | ?-0.0012 | ?0.1205 | ?-4.7599 | ?93.614 | [41，83] |
| Q 2/I/A/T | ?0 | ?7E-07 | ?-0.0001 | ?0.0058 | ?-0.113 | ?0.8709 | ?62.273 | [7，54.09] |
| Q 2/I/β/C | ?0 | ?0 | ?9E-08 | ?-3E-05 | ?0.0002 | ?0.0246 | ?41.062 | [0，100] |
| Q 2/I/β/T | ?0 | ?0 | ?-6E-07 | ?0.0001 | ?-0.0126 | ?0.5887 | ?23.694 | [0，100] |
Wherein: I: impeller
D: housing or Diffuser
A: vane region is arranged
NA: on-bladed district
T: wheel cap
C: wheel hub
β: β angle
In the laboratory, done repeatedly test to the known efficient of motor-drive pump with to efficient by the model machine of the geometrical shape exploitation that is fit to listed polynomial element.
As an example, enclose 13 test results of different flow rate Q below, in these examples, all new motor-drive pumps adopt same housing-Diffuser, the flow rate Q scope of first kind of impeller be the 3250-5700 liter/minute, the flow rate Q of second kind of impeller
2Scope be the 5000-7000 liter/minute.
| ??Q 1 | Old-fashioned hydraulic efficiency | New-type hydraulic efficiency |
| ??3250 | ????69.64 | ????75.164 |
| ??3750 | ????75.2 | ????80.33 |
| ??4250 | ????78.2 | ????86 |
| ??4500 | ????79.15 | ????87.2 |
| ??4800 | ????80.3 | ????88.37 |
| ??5100 | ????80.4 | ????87.5 |
| ??5400 | ????79.9 | ????85 |
| ??5700 | ????77.5 | ????82.4 |
| ??Q 2 | Old-fashioned hydraulic efficiency | New-type hydraulic efficiency |
| ??5000 | ????75 | ????85.43 |
| ??5500 | ????78 | ????86.7 |
| ??6000 | ????79 | ????86.2 |
| ??6500 | ????76.5 | ????83.7 |
| ??7000 | ????72 | ????79.366 |
Claims (3)
1, multi-stage motor pump group, it is made up of direct-connected motor by multistage centrifugal pump with pump, each level comprises pump, be impeller and Diffuser, their passage branch has vane region and on-bladed district, the border in these two districts is wheel cap surface and hub surface, the β angle is the surperficial each point angle of contingence, it is characterized in that the Y-axis that makes motor-drive pump is a y coordinate, X-axis is an abscissa, then for flow Q scope be the 2500-8000 liter/minute, the surperficial each point of impeller and Diffuser meets six rank multinomial Y=f (x)=AX
6+ BX
5+ CX
4+ DX
3+ EX
2+ FX+G, wherein on Diffuser:
A). wheel hub on-bladed district: A=B=C=D=E=0, F=0.6605, G=20.45;
B). wheel cap on-bladed district: A=B=C=D=E=0, F=0.7225, G=55.648;
C). wheel hub has vane region: A=9E-09, B=7E-06, C=-0.0019, D=0.3064,
E＝-26.923，F＝1256.3，G＝-24283；
D). wheel is stamped vane region: A=1E-10, B=-9E-08, C=2E-05, D=-0.0033,
E＝0.2349，F＝-7.616，G＝174.28；
E). wheel hub on-bladed district: A=0, B=0, C=-1E-05, D=0.0073, E=-1.7542,
F＝186.27，G＝-7311.6；
F). wheel cap on-bladed district: A=0, B=0, C=0, D=0.0053, E=-2.6745, F=446.37,
-G＝24717；
G). wheel hub β: A=0, B=0, C=1E-06, D=-0.0002, E=0.0203, F=-1.0819,
G＝156.82；
H). wheel cap β: A=0, B=0, C=3E-07, D=-1E-04, E=0.0101, F=-0.7587,
G＝175。
2, require described multi-stage motor pump according to aforesaid right, it is characterized in that, on the impeller:
A1). wheel hub on-bladed district: A=0, B=0, C=0, D=6E-05, E=0.0014, F=-0.0146,
G＝27.511；
B1). wheel cap on-bladed district: A=0, B=0, C=0, D=0, E=0, F=0, G=64.5;
C1). wheel hub has vane region: A=0, B=0, C=5E-06, D=-0.0014, E=0.1535,
F＝-6.3821，G＝121.24；
D1). wheel is stamped vane region: A=-4E-08, B=8E-06, C=-0.0006, D=0.0247,
E＝-0.4771，F＝4.3023，G＝50.015；
E1). wheel hub β: A=0, B=3E-09, C=-9E-07, D=0.0001, E=-0.0042,
F＝-0.0915，G＝34.402；
F1). wheel cap β: A=0, B=1E-09, C=-5E-07, D=6E-05,
E＝-0.0044，F＝0.1822，G＝22.2
3, multi-stage motor pump according to claim 1 is characterized in that, on the impeller:
A2). wheel hub on-bladed district: A=0, B=0, C=0, D=5E-05, E=0.0013,
F＝-0.0139，G＝27.511
B2). wheel cap on-bladed district: A=0, B=0, C=0, D=0, E=0, F=0, G=64.5
C2). wheel hub has vane region: A=0, B=0, C=5E-06, D=--0.0012, E=0.1205,
F＝--4.7599，G＝93.614；
D2). wheel is stamped vane region: A=-0, B=7E-07, C=-0.0001, D=0.0058,
E＝-0.113，F＝0.8709，G＝62.273；
E2). wheel hub β: A=0, B=0, C=9E-08, D=-3E-05, E=0.0002,
F＝0.0246，G＝41.062
F2). wheel cap β: A=0, B=0, C=-6E-07, D=0.0001, E=-0.0126,
F＝0.5887，G＝23.694。
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| ES200300601 | 2003-03-13 | ||
| ES200300601A ES2268912B1 (en) | 2003-03-13 | 2003-03-13 | MULTIETAPA ELECTRIC PUMP GROUP. |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN1530555A true CN1530555A (en) | 2004-09-22 |
Family
ID=32947016
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CNA2003101134433A Pending CN1530555A (en) | 2003-03-13 | 2003-11-10 | Multistage electric pump set |
Country Status (5)
| Country | Link |
|---|---|
| US (1) | US20040179949A1 (en) |
| CN (1) | CN1530555A (en) |
| ES (1) | ES2268912B1 (en) |
| IT (1) | ITMI20032065A1 (en) |
| MX (1) | MXPA04001132A (en) |
Families Citing this family (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102465882A (en) * | 2010-11-10 | 2012-05-23 | 上海福思特流体机械有限公司 | Multistage centrifugal pump with improved impeller arrangement |
| CN104179727B (en) * | 2013-05-22 | 2019-02-05 | 德昌电机(深圳)有限公司 | Pump |
| US9574562B2 (en) | 2013-08-07 | 2017-02-21 | General Electric Company | System and apparatus for pumping a multiphase fluid |
| US20180225409A1 (en) * | 2014-01-14 | 2018-08-09 | Charles C. Solvason | Performance analysis and monitoring of radial turbomachinery |
| CN113464497B (en) * | 2021-06-24 | 2024-09-20 | 珠海格力电器股份有限公司 | Diffuser, compressor and air cycle machine |
Family Cites Families (10)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| FR2536365A1 (en) * | 1982-11-18 | 1984-05-25 | Onera (Off Nat Aerospatiale) | BLADE FOR AIRCRAFT PROPELLER |
| CN1009017B (en) * | 1988-02-12 | 1990-08-01 | 中国科学院工程热物理研究所 | Submersible pump |
| FR2628062B1 (en) * | 1988-03-07 | 1990-08-10 | Aerospatiale | BLADE FOR HIGH PERFORMANCE FAIRED PROPELLER, MULTI-BLADE PROPELLER PROVIDED WITH SUCH BLADES AND TAIL ROTOR ARRANGEMENT WITH FAIRED PROPELLER FOR A TURNED AIRCRAFT |
| JPH0646035B2 (en) * | 1988-09-14 | 1994-06-15 | 株式会社日立製作所 | Multi-stage centrifugal compressor |
| US5375976A (en) * | 1990-07-27 | 1994-12-27 | Institut Francais Du Petrole | Pumping or multiphase compression device and its use |
| EP0571739B1 (en) * | 1992-05-28 | 1997-10-15 | Nikkiso Co., Ltd. | Axial diffusor for a centrifugal pump |
| US5961289A (en) * | 1995-11-22 | 1999-10-05 | Deutsche Forshungsanstalt Fur Luft-Und Raumfahrt E.V. | Cooling axial flow fan with reduced noise levels caused by swept laminar and/or asymmetrically staggered blades |
| JP3488718B2 (en) * | 1996-03-06 | 2004-01-19 | 株式会社日立インダストリイズ | Centrifugal compressors and diffusers for centrifugal compressors |
| JPH11173296A (en) * | 1997-12-11 | 1999-06-29 | Ebara Corp | Diffuser device for pump |
| US6739835B2 (en) * | 2001-08-24 | 2004-05-25 | Lg Electronics Inc. | Blade part in turbofan |
-
2003
- 2003-03-13 ES ES200300601A patent/ES2268912B1/en not_active Withdrawn - After Issue
- 2003-10-22 US US10/691,181 patent/US20040179949A1/en not_active Abandoned
- 2003-10-23 IT IT002065A patent/ITMI20032065A1/en unknown
- 2003-11-10 CN CNA2003101134433A patent/CN1530555A/en active Pending
-
2004
- 2004-02-04 MX MXPA04001132A patent/MXPA04001132A/en unknown
Also Published As
| Publication number | Publication date |
|---|---|
| ES2268912B1 (en) | 2008-02-16 |
| ITMI20032065A1 (en) | 2004-09-14 |
| US20040179949A1 (en) | 2004-09-16 |
| ES2268912A1 (en) | 2007-03-16 |
| MXPA04001132A (en) | 2004-09-15 |
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