WO2020164168A1 - 一种基于轴距的轴流泵叶轮设计方法 - Google Patents
一种基于轴距的轴流泵叶轮设计方法 Download PDFInfo
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- WO2020164168A1 WO2020164168A1 PCT/CN2019/077064 CN2019077064W WO2020164168A1 WO 2020164168 A1 WO2020164168 A1 WO 2020164168A1 CN 2019077064 W CN2019077064 W CN 2019077064W WO 2020164168 A1 WO2020164168 A1 WO 2020164168A1
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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
- F04D29/18—Rotors
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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
- F04D3/00—Axial-flow pumps
- F04D3/005—Axial-flow pumps with a conventional single stage rotor
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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
- F04D29/02—Selection of particular materials
- F04D29/026—Selection of particular materials 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
- F04D29/18—Rotors
- F04D29/181—Axial flow rotors
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- G—PHYSICS
- G06—COMPUTING; CALCULATING OR COUNTING
- G06F—ELECTRIC DIGITAL DATA PROCESSING
- G06F30/00—Computer-aided design [CAD]
- G06F30/10—Geometric CAD
- G06F30/17—Mechanical parametric or variational design
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
- F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
- F05D2240/00—Components
- F05D2240/20—Rotors
- F05D2240/30—Characteristics of rotor blades, i.e. of any element transforming dynamic fluid energy to or from rotational energy and being attached to a rotor
- F05D2240/301—Cross-sectional characteristics
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- G—PHYSICS
- G06—COMPUTING; CALCULATING OR COUNTING
- G06F—ELECTRIC DIGITAL DATA PROCESSING
- G06F2113/00—Details relating to the application field
- G06F2113/08—Fluids
Definitions
- the invention belongs to the field of fluid machinery design, and particularly relates to a design method of an axial flow pump impeller based on a wheelbase.
- Pumping stations and sluices are important components of water conservancy, environmental protection, urban water supply and drainage, and corporate water affairs. Pumps are irrigation and drainage equipment, and sluices are low-head hydraulic structures that regulate water levels and control flow.
- Traditional pump gate construction usually uses a combination of axial flow pumps and sluices, that is, along the cross-section of the river, a gate is arranged in the middle, and a pump is arranged on each side of the gate.
- the separation design of the pump and the gate of this kind of pump gate results in the traditional pump gate displacement being much lower than actual needs.
- Flood seasons are often unable to carry out flood drainage in time and effectively, and the efficiency of river water exchange and pollution control is far lower than the ideal value.
- the layout also restricts the cross-section of the river, slows down the flow of the river, is unfavorable to the water exchange and water circulation of the inland river, cannot meet the requirements of the inland river water ecological environment, and weakens the river's self-purification ability.
- the new integrated pump gate the pump unit is directly arranged on the gate.
- the gate is not only the water retaining structure but also the foundation of the pump support, so that the gate and the pump station are combined into one.
- the integrated pump gate has the following advantages: (1) The pump is installed vertically on the gate, and no additional pump chamber is required. When the gate is lifted, the flow area of the river can be increased by more than double, and the gate is dropped. The time pump can significantly increase the drainage speed; (2) Only the power distribution room, water pump, gate and flapping door are needed. The main workshop is not built, and there is no auxiliary oil, water, and gas system.
- the area is small, and the construction is convenient and fast, thereby reducing The investment in civil engineering and electromechanical equipment of the pumping station is improved; (3) By installing auxiliary facilities such as the liquid level control system and the automatic gate control system, the entire system can be linked and controlled, truly unattended and automatic control, which greatly reduces the late stage of the pump gate. Personnel maintenance costs.
- the design of integrated pump gates mostly focuses on optimizing the gate structure and improving the flow conditions of the front and rear pools; axial flow pumps, as the key power equipment of integrated pump gates, are generally directly selected from existing products.
- the integrated pump gate due to the limitation of gate thickness, the integrated pump gate requires the axial length of the axial flow pump to be as short as possible. If the axial length of the axial flow pump is too large and the gate is thicker, the design, manufacturing, operation and maintenance costs of the integrated pump gate will be greatly increased, and the response speed of the gate will also be greatly reduced. This makes the existing axial flow pump products unable to well meet the structure and performance requirements of the integrated pump gate.
- the present invention provides a design method of axial flow pump impeller based on wheelbase.
- the purpose of the present invention is to provide a design method of axial flow pump impeller based on wheelbase, which includes the following steps:
- L 1 is the axial length required by the design; the axial length of the outermost section of L w ; select the axial flow pump impeller parameter airfoil chord length l, blade chord placement angle ⁇ L is the reference parameter to determine the impeller diameter D, hub diameter d h , and pitch t;
- step S1 the airfoil chord length l and the blade placement angle ⁇ L are determined by the flow Q, the head H, and the rotation speed n.
- the calculation method is as follows:
- the airfoil chord length l c is determined by the airfoil chord length l w of the outermost section;
- the outermost section is section 6; when the impeller section number is 5, the outermost section is section 5; when the impeller section number is 4, the outermost section is section 4;
- a is the correction coefficient, and the value method is as follows;
- chord length l c of the airfoil section is determined by the following general formula:
- a 1 is the proportional coefficient, and the specific values are shown in the following table:
- the blade setting angle ⁇ Lc of the airfoil section is determined by the outermost blade setting angle ⁇ Lw ;
- V m1 inlet axial velocity; V m2 outlet axial velocity; u circumferential velocity; V u2 rotational speed; ⁇ 1 blade inlet angle; blade outlet angle; b is the correction coefficient, which is determined by the specific speed;
- the airfoil section blade placement angle ⁇ Lc is determined by the following general formula:
- b 1 is the proportional coefficient, and the specific values are shown in the following table:
- L 1 is the axial length required by the design
- L w is the axial length of the outermost section
- step (2) If L 1 ⁇ L and the error is greater than 5%, return to step (2) to reduce the value of correction coefficient a, or return to step (3) to reduce the value of correction coefficient b.
- step S2 the impeller diameter D, the hub diameter d h and the pitch t are determined by the airfoil chord length l and the blade placement angle ⁇ L ;
- the impeller diameter D c of each section is determined by the following general formula:
- the maximum diameter of the impeller D w is determined by the following general formula
- c is the proportional coefficient
- K is the correction coefficient
- specific values are shown in the table below;
- D w is the maximum diameter of the impeller, and the hub ratio Determined by specific speed n s +3.87 ⁇ sin ⁇ L ;
- step S3 select the 791 airfoil thickness change rule to thicken the blade
- the thickness of the 791 airfoil is used for thickening;
- the thickness change of the 791 airfoil is shown in the following table;
- x is the distance from the left edge of the airfoil, and
- ⁇ is the airfoil thickness ;
- the established design method based on the wheelbase axial flow pump impeller can provide a way to solve the development bottleneck of the integrated pump gate
- Fig. 1 is an axial sectional view of the impeller of embodiment 1.
- Figure 2 A sectional view of the blade.
- FIG. 1 Schematic diagram of airfoil thickening.
- FIG. 4 is a flowchart of the present invention.
- l is the chord length of the airfoil
- ⁇ L is the blade angle
- D impeller diameter
- d h is the hub diameter
- t is the pitch
- section 1 is a section of 2,3 to 1,2 3,4 to section Sections 4 and 5 are section 5
- x is the distance from the left edge of the airfoil
- ⁇ is the thickness of the airfoil
- ⁇ max is the maximum thickness of the airfoil.
- the error range is less than 5%, which meets the design requirements
- the thickness of the 791 airfoil is used for thickening
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- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Physics & Mathematics (AREA)
- Geometry (AREA)
- General Physics & Mathematics (AREA)
- Theoretical Computer Science (AREA)
- Pure & Applied Mathematics (AREA)
- Computer Hardware Design (AREA)
- Evolutionary Computation (AREA)
- Mathematical Optimization (AREA)
- Mathematical Analysis (AREA)
- Computational Mathematics (AREA)
- Structures Of Non-Positive Displacement Pumps (AREA)
Abstract
Description
比转速n s | n s≤450 | 450≤n s≤800 | 800≤n s |
叶轮断面数 | 4 | 5 | 6 |
比转速n s | n s≤600 | 600≤n s≤850 | 850≤n s≤1500 |
叶片数 | 5 | 4 | 3 |
叶片数z | 3 | 4 | 5 |
修正系数a(6个断面) | 4.2~6.3 | 6.3~8.9 | 8.9~10.2 |
修正系数a(5个断面) | 3.4~5.8 | 5.8~7.6 | 7.6~9.4 |
修正系数a(4个断面) | 2.8~5.5 | 5.5~7.3 | 7.3~8.9 |
比转速n s | 0~380 | 380~610 | 610~930 | 930~1500 |
修正系数b(6个断面) | 0.21~0.28 | 0.16~0.21 | 0.12~0.16 | 0.05~0.12 |
修正系数b(5个断面) | 0.19~0.24 | 0.13~0.19 | 0.08~0.13 | 0.03~0.08 |
修正系数b(4个断面) | 0.16~0.22 | 0.13~0.16 | 0.07~0.13 | 0.03~0.07 |
断面数 | 4 | 5 | 6 |
修正系数K | 19.3~22.45 | 17.8~20.14 | 15.8~19.6 |
x/l | 0 | 0.05 | 0.075 | 0.1 | 0.2 | 0.3 | 0.4 | 0.5 | 0.6 |
δ/δ max | 0 | 0.296 | 0.405 | 0.489 | 0.778 | 0.92 | 0.978 | 1.0 | 0.883 |
x/l | 0.7 | 0.8 | 0.9 | 0.95 | 1.0 |
δ/δ max | 0.756 | 0.544 | 0.356 | 0.2 | 0 |
比转速n s | n s≤450 | 450≤n s≤800 | 800≤n s |
叶轮断面数 | 4 | 5 | 6 |
比转速n s | 0~600 | 600~850 | 850~1500 |
叶片数z | 3 | 4 | 5 |
叶片数z | 3 | 4 | 5 |
修正系数a | 3.4~5.8 | 5.8~7.6 | 7.6~9.4 |
比转速n s | 0~380 | 380~610 | 610~930 | 930~1500 |
修正系数b | 0.19~0.24 | 0.13~0.19 | 0.08~0.13 | 0.03~0.08 |
x/l | 0 | 0.05 | 0.075 | 0.1 | 0.2 | 0.3 | 0.4 | 0.5 | 0.6 |
δ | 0 | 4.017 | 5.496 | 6.636 | 10.557 | 12.484 | 13.271 | 13.57 | 11.982 |
x/l | 0.7 | 0.8 | 0.9 | 0.95 | 1.0 |
δ | 10.259 | 7.382 | 4.831 | 2.714 | 0 |
x/l | 0 | 0.05 | 0.075 | 0.1 | 0.2 | 0.3 | 0.4 | 0.5 | 0.6 |
δ | 0 | 3.514 | 4.807 | 5.804 | 9.235 | 10.920 | 11.609 | 11.87 | 10.481 |
x/l | 0.7 | 0.8 | 0.9 | 0.95 | 1.0 |
δ | 8.974 | 6.457 | 4.226 | 2.374 | 0 |
x/l | 0 | 0.05 | 0.075 | 0.1 | 0.2 | 0.3 | 0.4 | 0.5 | 0.6 |
δ | 0 | 3.001 | 4.114 | 4.968 | 7.904 | 9.347 | 9.936 | 10.16 | 8.971 |
x/l | 0.7 | 0.8 | 0.9 | 0.95 | 1.0 |
δ | 7.112 | 8.128 | 9.144 | 9.652 | 10.16 |
x/l | 0 | 0.05 | 0.075 | 0.1 | 0.2 | 0.3 | 0.4 | 0.5 | 0.6 |
δ | 0 | 2.504 | 3.426 | 4.137 | 6.582 | 7.783 | 8.274 | 8.46 | 7.470 |
x/l | 0.7 | 0.8 | 0.9 | 0.95 | 1.0 |
δ | 5.922 | 6.768 | 7.614 | 8.037 | 8.46 |
x/l | 0 | 0.05 | 0.075 | 0.1 | 0.2 | 0.3 | 0.4 | 0.5 | 0.6 |
δ | 0 | 0.648 | 0.887 | 1.071 | 1.704 | 2.015 | 2.142 | 2.19 | 1.934 |
x/l | 0.7 | 0.8 | 0.9 | 0.95 | 1.0 |
δ | 1.533 | 1.752 | 1.971 | 2.081 | 2.19 |
Claims (4)
- 一种基于轴距的轴流泵叶轮设计方法,其特征在于,包含以下具体步骤:(S1)以轴流泵叶轮轴向长度L设计函数L=l×sinβ L为设计基础,根据给定的轴流泵设计流量Q、扬程H、转速n、比转速n s设计参数,从叶轮轮毂至叶轮外缘等间距划分断面,通过比转速n s确定断面数和叶片数;然后确定轴流泵叶轮轴向长度L的翼型弦长l和叶片安放角β L;(S2)当L 1/L w=0.95~1;其中,L 1为设计要求轴向长度;L w最外侧断面的轴向长度;选取轴流泵叶轮参数翼型弦长l,叶片安放角β L为基准参数,确定叶轮直径D,轮毂直径d h,节距t;(S3)以翼型弦长l为基准,选择791翼型厚度变化规律进行加厚。
- 根据权利要求1所述的一种基于轴距的轴流泵叶轮设计方法,其特征在于:步骤S1中,通过流量Q、扬程H、转速n确定翼型弦长l和叶片安放角β L,计算方法如下:(1)根据比转速n s确定叶轮设计断面数量和叶片数:将轴流泵叶轮分为4~6个断面,从叶轮轮毂至叶轮外缘等间距划分断面;断面数和叶片数通过比转速n s确定;当比转速n s≤450时,叶轮断面数为4;当比转速450≤n s≤800时,叶轮断面数为5;当比转速800≤n s时,叶轮断面数为6;当比转速n s≤600时,叶片数为5;当比转速600≤n s≤850时,叶片数为4;当比转速850≤n s≤1500时,叶片数为3;(2)根据升力法计算翼型弦长l,翼型断面翼型弦长l c通过最外侧断面翼型弦长l w确定;当叶轮断面数为6时,最外侧断面即为断面6;当叶轮断面数为5时,最外侧断面即为断面5;当叶轮断面数为4时,最外侧断面即为断面4;其中,a为修正系数,取值方法如下所示;当断面数为6,叶片数z为3时,修正系数a=4.2~6.3,当断面数为6,叶片数z为4时,修正系数a=6.3~8.9,当断面数为6,叶片数z为5时,修正系数a=8.9~10.2,当断面数为5,叶片数z为3时,修正系数a=3.4~5.8,当断面数为5,叶片数z为4时,修正系数a=5.8~7.6,当断面数为5,叶片数z为5时,修正系数a=7.6~9.4,当断面数为4,叶片数z为3时,修正系数a=2.8~5.5,当断面数为4,叶片数z为4时,修正系数a=5.5~7.3,当断面数为4,叶片数z为5时,修正系数a=7.3~8.9,翼型断面翼型弦长l c通过以下通式确定:l c=a 1×l w其中,a 1为比例系数,具体取值如下所示:当断面数为4时,断面1的a 1为0.651~0.728,断面2的a 1为0.793~0.873,断面3的a 1为0.894~0.981,断面4的a 1为1,当断面数为5时,断面1的a 1为0.623~0.685,断面2的a 1为0.712~0.787,断面3的a 1为0.826~0.894,断面4的a 1为0.931~0.963,断面5的a 1为1,当断面数为6时,断面1的a 1为0.489~0.553,断面2的a 1为0.586~0.653,断面3的a 1为0.705~0.781,断面4的a 1为0.793~0.842,断面5的a 1为0.856~0.925,断面6的a 1为1;(3)根据升力法计算叶片安放角β L,翼型断面叶片安放角β Lc通过最外侧断面叶片安放角β Lw确定;最外侧断面叶片安放角β Lw的计算方法如下所示:其中,V m1进口轴面速度;V m2出口轴面速度;u圆周速度;V u2旋转分速度;β 1叶片进口角;叶片出口角;b为修正系数,通过比转速确定;在断面数为6的情况下,当比转速n s为0~380时,修正系数b为0.21~0.28;当比转速n s为380~610时,修正系数b为0.16~0.21;当比转速n s为610~930时,修正系数b为0.12~0.16;当比转速n s为930~1500时,修正系数b为0.05~0.12;在断面数为5的情况下,当比转速n s为0~380时,修正系数b为0.19~0.24;当比转速n s为380~610时,修正系数b为0.13~0.19;当比转速n s为610~930时,修正系数b为0.08~0.13;当比转速n s为930~1500时,修正系数b为0.03~0.08;在断面数为4的情况下,当比转速n s为0~380时,修正系数b为0.16~0.22;当比转速n s为380~610时,修正系数b为0.13~0.16;当比转速n s为610~930时,修正系数b为0.07~0.13;当比转速n s为930~1500时,修正系数b为0.03~0.07;翼型断面叶片安放角β Lc通过以下通式确定:β Lc=b 1×β Lw其中,b 1为比例系数,具体取值如下所示:当断面数为4时,断面1的b 1为1.92~2.24,断面2的b 1为1.52~1.73,断面3的b 1为1.36~1.56,断面4的b 1为1,当断面数为5时,断面1的b 1为1.84~2.18,断面2的b 1为1.43~1.68,断面3的b 1为1.22~1.34,断面4的b 1为1.06~1.15,断面5的b 1为1,当断面数为6时,断面1的b 1为1.72~2.06,断面2的b 1为1.21~1.53,断面3的b 1为1.17~1.42,断面4的b 1为0.97~1.21,断面5的b 1为0.83~0.92,断面6的b 1为1。(4)通过L=l×sinβ L确定轴流泵叶轮的轴向长度;L 1为设计要求轴向长度;L w最外侧断面的轴向长度;设计误差允许范围为5%,即L 1/L w=0.95~1;若L 1>Lw且误差大于5%,则返回步骤(2)增大修正系数a的取值,或者返回步骤(3)增加修正系数b的取值;若L 1<Lw且误差大于5%,则返回步骤(2)减小修正系数a的取值,或者返回步骤(3)减小修正系数b的取值。
- 根据权利要求1或2所述的一种基于轴距的轴流泵叶轮设计方法,其特征在于:步骤S2中,通过翼型弦长l和叶片安放角β L确定叶轮直径D,轮毂直径d h,节距t,计算方法如下:(1)叶轮直径D各断面的叶轮直径D c通过以下通式确定;叶轮最大直径D w通过以下通式确定其中,c为比例系数,K为修正系数,具体取值如下所示;当断面数为4时,修正系数K为19.3~22.45;断面1的比例系数c为0.5,断面2的比例系数c为0.64,断面3的比例系数c为0.76,断面4的比例系数c为0.98;当断面数为5时,修正系数K为17.8~20.14;断面1的比例系数c为0.5,断面2的比例系数c为0.61,断面3的比例系数c为0.73,断面4的比例系数c为0.85,断面5的比例系数c为0.97;当断面数为6时,修正系数K为15.8~19.6;断面1的比例系数c为0.5,断面2的比例系数c为0.53,断面3的比例系数c为0.57,断面4的比例系数c为0.69,断面5的比例系数c为0.82,断面6的比例系数c为0.93;(2)叶轮轮毂直径d h(3)节距t各断面节距t c通过以下通式确定;
- 根据权利要求1所述的一种基于轴距的轴流泵叶轮设计方法,其特征在于:步骤S3中,选择791翼型厚度变化规律进行加厚;(1)最大翼型厚度δ max(2)以翼型弦长l为基准,采用791翼型厚度变化规律进行加厚;791翼型厚度变化规律如下所示;x为距翼型左侧边缘的距离,δ为翼型厚度;当x/l为0时,δ/δ max为0;当x/l为0.05时,δ/δ max为0.296;当x/l为0.075时,δ/δ max为0.405;当x/l为0.1时,δ/δ max为0.489;当x/l为0.2时,δ/δ max为0.778;当x/l为0.3时,δ/δ max为0.92;当x/l为0.4时,δ/δ max为0.978;当x/l为0.5时,δ/δ max为1.0;当x/l为0.6时,δ/δ max为0.883;当x/l为0.7时,δ/δ max为0.756;当x/l为0.8时,δ/δ max为0.544;当x/l为0.9时,δ/δ max为0.356;当x/l为0.95时,δ/δ max为0.2;当x/l为1.0时,δ/δ max为0;(3)加厚时,以型线为工作面向背面加厚。
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GB2012612.4A GB2593558B (en) | 2019-02-13 | 2019-03-06 | Method for designing axial-flow pump impeller based on axial distance |
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CN113935126A (zh) * | 2021-09-10 | 2022-01-14 | 南京磁谷科技股份有限公司 | 一种磁悬浮风机工作效率优化方法 |
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CN109236726A (zh) * | 2018-07-31 | 2019-01-18 | 江苏大学镇江流体工程装备技术研究院 | 一种高比转速轴流泵叶轮出口角和厚度设计方法 |
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CN113935126B (zh) * | 2021-09-10 | 2023-03-07 | 南京磁谷科技股份有限公司 | 一种磁悬浮风机工作效率优化方法 |
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