CN106202795A - Centrifugal pump impeller and the method for designing thereof of constraint is combined based on entropy product and blade loading - Google Patents
Centrifugal pump impeller and the method for designing thereof of constraint is combined based on entropy product and blade loading Download PDFInfo
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Abstract
本发明涉及基于熵产和叶片载荷联合约束的离心泵叶轮及其设计方法。目的是提供的方法能够提高设计效率，提供的离心泵叶轮可以降低离心泵能量损失。技术方案是：一种基于熵产和叶片载荷联合约束的离心泵叶轮设计方法，其特征在于，包括以下步骤：1)确定流道叶片载荷分布；2)绘制出叶片几何模型；3)验证是否符合物理要求；4)若叶片模型不满足物理要求，则返回步骤1)重新绘制叶片；5)计算出叶片的能量损失分布情况；6)开至少一个圆形的平衡孔；7)进行CFD仿真验证。一种离心泵叶轮：包含六个叶片，每个叶片上分别开有平衡孔，平衡孔位于叶片轴向的中截面位置，平衡孔的中心到叶片进口的距离为叶片长度的70％～80％。
The invention relates to a centrifugal pump impeller and a design method thereof based on joint constraints of entropy production and blade load. The purpose is that the provided method can improve the design efficiency, and the provided centrifugal pump impeller can reduce the energy loss of the centrifugal pump. The technical solution is: a centrifugal pump impeller design method based on the combined constraints of entropy production and blade load, which is characterized in that it includes the following steps: 1) determining the flow channel blade load distribution; 2) drawing the blade geometric model; 3) verifying whether Meet the physical requirements; 4) If the blade model does not meet the physical requirements, return to step 1) redraw the blade; 5) Calculate the energy loss distribution of the blade; 6) Open at least one circular balance hole; 7) Perform CFD simulation verify. A centrifugal pump impeller: including six blades, each of which is provided with a balance hole, the balance hole is located at the axial middle section of the blade, and the distance from the center of the balance hole to the blade inlet is 70% to 80% of the blade length .
Description
技术领域technical field
本发明涉及离心泵叶轮技术领域，具体是一种基于熵产和叶片载荷联合约束的离心泵叶轮设计方法，以及一种离心泵叶轮。The invention relates to the technical field of centrifugal pump impellers, in particular to a centrifugal pump impeller design method based on combined constraints of entropy production and blade load, and a centrifugal pump impeller.
背景技术Background technique
离心泵内部复杂的三维非定常湍流，常导致一些影响离心泵运行特性的不良现象，如压力脉动、流动分离、水力振动等，严重影响机组的运转稳定性及工作寿命。The complex three-dimensional unsteady turbulent flow inside the centrifugal pump often leads to some adverse phenomena that affect the operating characteristics of the centrifugal pump, such as pressure pulsation, flow separation, hydraulic vibration, etc., which seriously affect the operation stability and working life of the unit.
目前，传统的离心泵设计方法在对离心泵进行设计时，都是定义叶片几何，然后进行CFD仿真，反复实验性地修改叶片几何，且CFD计算结果和如何修改叶片几何无必然联系，其中大部分修改是错误的或者多余的，主要依赖工程师的设计经验，造成时间和人力的浪费。At present, the traditional centrifugal pump design method is to define the blade geometry when designing a centrifugal pump, then perform CFD simulation, and repeatedly modify the blade geometry experimentally, and there is no necessary connection between the CFD calculation results and how to modify the blade geometry. Some modifications are wrong or redundant, mainly relying on the design experience of engineers, resulting in a waste of time and manpower.
发明内容Contents of the invention
本发明要解决的技术问题是克服上述背景技术的不足，提供一种离心泵叶轮设计方法，能够提高设计效率，节省设计成本，根据该设计方法设计的离心泵叶轮，可以在保障扬程和效率的同时，降低离心泵能量损失，以提高离心泵的寿命及运转稳定性。The technical problem to be solved by the present invention is to overcome the deficiencies of the above-mentioned background technology, and provide a centrifugal pump impeller design method, which can improve design efficiency and save design cost. The centrifugal pump impeller designed according to the design method can ensure the lift and efficiency. At the same time, the energy loss of the centrifugal pump is reduced to improve the service life and operation stability of the centrifugal pump.
本发明采用的技术方案是：一种基于熵产和叶片载荷联合约束的离心泵叶轮设计方法，其特征在于，包括以下步骤：The technical scheme adopted in the present invention is: a centrifugal pump impeller design method based on the combined constraints of entropy production and blade load, characterized in that it includes the following steps:
1)在计算机的CFD系统中对原型泵进行仿真，根据计算公式确定流道叶片载荷分布；1) Simulate the prototype pump in the CFD system of the computer, according to the calculation formula Determine the flow path blade load distribution;
式中：p+和p-分别为叶片压力面和吸力面压力，单位Pa；z为叶片数；Wmbl为叶片流线上的相对速度，单位m/s；ρ为水的密度；为速度环量，单位m2/s；m为相对轴面流线长度；为叶片载荷；In the formula: p + and p - are the pressure on the pressure surface and the suction surface of the blade, respectively, in Pa; z is the number of blades; W mbl is the relative velocity on the blade streamline, in m/s; ρ is the density of water; is the velocity circulation, the unit is m 2 /s; m is the streamline length relative to the axial surface; is the blade load;
2)根据载荷分布情况，在确定两条叶片载荷曲线后，根据叶片型线微分方程绘制出叶片几何模型；2) According to the load distribution, after determining the two blade load curves, according to the differential equation of the blade profile Draw the geometric model of the blade;
3)对绘制出的叶片几何模型进行CFD仿真验证是否符合物理要求；3) Perform CFD simulation on the drawn blade geometry model to verify whether it meets the physical requirements;
4)若叶片模型不满足物理要求，则返回步骤1)，调整叶片载荷分布，重新绘制叶片；4) If the blade model does not meet the physical requirements, return to step 1), adjust the blade load distribution, and redraw the blade;
5)若设计的叶轮满足物理要求，则基于能量熵理论，根据公式计算出叶片的能量损失分布情况；5) If the designed impeller meets the physical requirements, based on the energy entropy theory, according to the formula Calculate the energy loss distribution of the blade;
S″′D的值由雷诺平均N-S方程获得，S″′D′可由式得出，其中κ和ω分别是SSTκ-ω模型中的湍动能和特征频率,α＝0.09为经验常数，V代表流道体积，T为离心泵内部温度；The value of S″′ D is obtained by the Reynolds average NS equation, and S″′ D′ can be obtained by the formula It is obtained that κ and ω are the turbulent kinetic energy and characteristic frequency in the SSTκ-ω model respectively, α=0.09 is an empirical constant, V represents the flow channel volume, and T is the internal temperature of the centrifugal pump;
6)根据叶片的能量损失分布情况，在叶片上发生能量损失的主要位置开至少一个圆形的平衡孔，平衡孔半径为叶片出口端宽度的1/5～1/6，平衡孔轴向位置位于叶片中截面；6) According to the energy loss distribution of the blade, open at least one circular balance hole at the main position where energy loss occurs on the blade. The radius of the balance hole is 1/5~1/6 of the width of the blade outlet end, and the axial position of the balance hole Located in the middle section of the blade;
7)对开孔后的叶片模型进行CFD仿真验证，若叶片的能量损失仍不满足要求，则改变叶片载荷分布，返回步骤2)，直到设计出满足能量损失要求的叶片为止。7) Perform CFD simulation verification on the blade model after hole opening. If the energy loss of the blade still does not meet the requirements, change the blade load distribution and return to step 2) until a blade that meets the energy loss requirements is designed.
作为优选，一种离心泵叶轮，其特征在于：包含六个叶片，每个叶片上分别开有平衡孔，平衡孔半径为4～5mm，所述平衡孔位于叶片轴向的中截面位置，平衡孔的中心到叶片进口的距离为叶片长度的70％～80％。As a preference, a centrifugal pump impeller is characterized in that it includes six blades, each blade is respectively provided with a balance hole, the radius of the balance hole is 4-5mm, and the balance hole is located at the mid-section position of the blade axial direction. The distance from the center of the hole to the blade inlet is 70%-80% of the blade length.
作为优选，所述叶片厚度为2～3mm，叶片进口直径为300～320mm，叶片出口直径为600～640mm,叶片出口的宽度为20～25mm,叶片进口安放角为29-30度，叶片出口安放角为20～24度。Preferably, the thickness of the blade is 2-3 mm, the diameter of the blade inlet is 300-320 mm, the diameter of the blade outlet is 600-640 mm, the width of the blade outlet is 20-25 mm, the angle of the blade inlet is 29-30 degrees, and the blade outlet is placed The angle is 20-24 degrees.
本发明的有益效果是：The beneficial effects of the present invention are:
1)采用能量熵的方法，分析出叶轮能量损失的主要区域，为载荷分布的调整提供参考；1) Using the method of energy entropy, the main area of impeller energy loss is analyzed to provide reference for the adjustment of load distribution;
2)基于熵产和叶片载荷理论联合约束，来求解离心泵水力设计问题，提高了设计效率，缩短了离心泵设计周期；2) Based on the combined constraints of entropy production and blade load theory, the hydraulic design problem of centrifugal pumps is solved, which improves the design efficiency and shortens the design cycle of centrifugal pumps;
3)基于叶片载荷理论的全三维反设计方法，通过调整叶片载荷分布计算出满足最优化的流量分布的叶片几何，大幅提高设计速度，节省大量人力和时间；3) The full three-dimensional inverse design method based on the blade load theory calculates the blade geometry that satisfies the optimal flow distribution by adjusting the blade load distribution, which greatly improves the design speed and saves a lot of manpower and time;
4)不再强烈依赖于工程师的设计经验，新手也可尝试进行设计；4) It is no longer strongly dependent on the design experience of engineers, and novices can also try to design;
5)通过本优化设计方法设计的叶轮，能有效的降低离心泵的能量损失，提高泵的运转稳定性和运行寿命。5) The impeller designed by this optimal design method can effectively reduce the energy loss of the centrifugal pump and improve the operation stability and service life of the pump.
附图说明Description of drawings
图1是本发明所述设计方法的设计流程图；Fig. 1 is the design flowchart of design method of the present invention;
图2是叶轮轴面剖视图；Figure 2 is a cross-sectional view of the impeller shaft;
图3是叶轮主视图；Fig. 3 is the front view of impeller;
图4是叶片载荷曲线；Fig. 4 is the blade load curve;
图5是叶轮优化前后性能曲线对比图；Figure 5 is a comparison chart of performance curves before and after impeller optimization;
图6是叶轮优化前后能量损失分布对比图。Figure 6 is a comparison chart of energy loss distribution before and after impeller optimization.
其中：1、叶片；2、平衡孔；3、前盖板；4、流道；5、后盖板；6、转轴。Among them: 1. blade; 2. balance hole; 3. front cover plate; 4. flow channel; 5. rear cover plate; 6. rotating shaft.
具体实施方式detailed description
下面对本发明作进一步说明，但本发明并不局限于以下实施例。The present invention will be further described below, but the present invention is not limited to the following examples.
参见图1到图6，本发明提供的一种基于熵产和叶片载荷联合约束的离心泵叶轮设计方法，其原型泵设计流量为Qd＝0.008m3/s,Hd＝0.1m,n＝40r/min。Referring to Fig. 1 to Fig. 6, the present invention provides a centrifugal pump impeller design method based on the joint constraint of entropy production and blade load, the design flow rate of the prototype pump is Q d =0.008m 3 /s, H d =0.1m,n =40r/min.
该设计方法包括以下步骤：The design method includes the following steps:
1)对现有的原型泵，在计算机的CFD系统中进行数值模拟(仿真),由根据计算公式计算出原型泵叶轮流道4靠近前盖板3、后盖板5位置的叶片载荷分布，从而根据叶片载荷分布情况确定靠近前盖板的叶片载荷曲线以及靠近后盖板的叶片载荷曲线，其前后盖板载荷分布为：前加载点m1＝0.38，后加载点m2＝0.82，中间主加载区斜率k＝0.8；式中：p+和p-分别为叶片压力面和吸力面压力，单位Pa；z为叶片数；Wmbl为叶片流线上的相对速度，单位m/s；ρ为水的密度；为速度环量，单位m2/s；m为相对轴面流线长度；为叶片载荷；1) For the existing prototype pump, carry out numerical simulation (simulation) in the CFD system of the computer, according to the calculation formula Calculate the blade load distribution of the prototype pump impeller channel 4 near the front cover 3 and the rear cover 5, so as to determine the blade load curve near the front cover and the blade load curve near the rear cover according to the blade load distribution. The load distribution of the front and rear cover plates is: the front loading point m1=0.38, the rear loading point m2=0.82, the slope of the middle main loading area k=0.8; where: p + and p - are the pressure on the pressure surface and the suction surface of the blade, respectively, in Pa ; z is the number of blades; W mbl is the relative velocity on the blade streamline, unit m/s; ρ is the density of water; is the velocity circulation, the unit is m 2 /s; m is the streamline length relative to the axial surface; is the blade load;
2)根据前后盖板的两条叶片载荷曲线(前盖板、后盖板各一条叶片载荷曲线)分布情况，由叶片型线微分方程绘制出叶片几何模型；式中：vm是轴面流速，f为叶片包角，ω为叶片旋转角速度，r为叶片上节点的半径，Vθ为节点的圆周分速度，s为轴面流线长度，2) According to the distribution of the two blade load curves of the front and rear shrouds (one blade load curve for the front shroud and the rear shroud), the differential equation of the blade shape line Draw the geometric model of the blade; where: v m is the axial surface flow velocity, f is the blade wrap angle, ω is the blade rotational angular velocity, r is the radius of the node on the blade, V θ is the circumferential component velocity of the node, and s is the axial surface flow line length,
3)对绘制出的叶片模型进行CFD仿真验证，其符合物理要求；3) Carry out CFD simulation verification on the drawn blade model, which meets the physical requirements;
4)由CFD系统计算结果，由以下公式计算离心泵内部能量损失S”'分布情况：4) From the calculation results of the CFD system, the distribution of the internal energy loss S"' of the centrifugal pump is calculated by the following formula:
总熵产生率为 The total entropy production rate is
式中：u代表沿x轴的速度分量，v代表沿y轴的速度分量，w代表沿z轴的速度分量，μ是动力粘度。In the formula: u represents the velocity component along the x-axis, v represents the velocity component along the y-axis, w represents the velocity component along the z-axis, μ is the dynamic viscosity.
式中，S″′D的值由雷诺平均N-S方程获得，S″′D′可由式得出，其中κ和ω分别是SSTκ-ω模型中的湍动能和特征频率,α＝0.09为经验常数，V代表流道体积，T为离心泵内部温度(离心泵内部为等温流动，T指的也是这个恒定的温度)；In the formula, the value of S″’ D is obtained by the Reynolds average NS equation, and S″’ D’ can be obtained by the formula It can be obtained that κ and ω are the turbulent kinetic energy and eigenfrequency in the SSTκ-ω model respectively, α=0.09 is an empirical constant, V represents the channel volume, T is the internal temperature of the centrifugal pump (the internal flow of the centrifugal pump is isothermal, T refers to is also this constant temperature);
通过分析计算，可得出总能量损失分布情况；Through analysis and calculation, the distribution of total energy loss can be obtained;
5)在轴向的叶片中截面(几何上的叶片轴向中间的位置)，径向相对叶片流线的75％长度位置处开半径为5mm的平衡孔2(即沿着叶片流线，平衡孔与叶片入口的距离为叶片流线总长度的75％位置)，通过平衡孔，冲散此区域不稳定流动涡，以降低能量损失；5) On the mid-section of the axial blade (geometrically, the position in the middle of the axial direction of the blade), a balance hole 2 with a radius of 5 mm is opened at a position radially opposite to 75% of the length of the blade streamline (that is, along the blade streamline, balanced The distance between the hole and the blade inlet is 75% of the total length of the blade streamline), through the balance hole, the unstable flow vortex in this area is washed away to reduce energy loss;
6)调整载荷曲线分布，对叶轮进行优化，当前加载点m1＝0.4,后加载点m2＝0.78,主加载区斜率k＝-4时，能量损失最小，同时可得出其能量损失分布情况；通过优化设计，设计出的叶轮其扬程和效率不降低的情况下，能量损失明显降低(降低10％到20％的能量损失)。6) Adjust the load curve distribution and optimize the impeller. When the current loading point m1=0.4, the rear loading point m2=0.78, and the slope k=-4 in the main loading area, the energy loss is the smallest, and the energy loss distribution can be obtained at the same time; By optimizing the design, the energy loss of the designed impeller is significantly reduced (10% to 20% energy loss) without reducing the lift and efficiency of the impeller.
本发明还提供一种根据上述设计方法设计的离心泵叶轮，包含转轴6以及六个叶片1，每个叶片上分别开有平衡孔2，平衡孔半径为4～5mm，所述平衡孔位于叶片轴向的中截面位置；沿着叶片流线，平衡孔的中心到叶片进口的距离为叶片长度的70～80％。The present invention also provides a centrifugal pump impeller designed according to the above design method. Axial mid-section position; along the blade streamline, the distance from the center of the balance hole to the blade inlet is 70-80% of the blade length.
所述叶片厚度为2～3mm，叶片进口直径为300～320mm，叶片出口直径为600～640mm,叶片出口的宽度为20～25mm,叶片进口安放角为29-30度，叶片出口安放角为20～24度。The blade thickness is 2-3 mm, the blade inlet diameter is 300-320 mm, the blade outlet diameter is 600-640 mm, the blade outlet width is 20-25 mm, the blade inlet placement angle is 29-30 degrees, and the blade outlet placement angle is 20 ~24 degrees.
最后，需要注意的是，以上列举的仅是本发明的具体实施例。显然，本发明不限于以上实施例，还可以有很多变形。本领域的普通技术人员能从本发明公开的内容中直接导出或联想到的所有变形，均应认为是本发明的保护范围。Finally, it should be noted that what is listed above are only specific embodiments of the present invention. Obviously, the present invention is not limited to the above embodiments, and many modifications are possible. All deformations that can be directly derived or associated by those skilled in the art from the content disclosed in the present invention should be considered as the protection scope of the present invention.
Claims (3)
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| CN110617238A (en) * | 2019-09-26 | 2019-12-27 | 浙江理工大学 | Optimization design method of centrifugal pump impeller |
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