WO2019075777A1 - 一种射流式自吸离心泵的优化设计方法 - Google Patents

一种射流式自吸离心泵的优化设计方法 Download PDF

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WO2019075777A1
WO2019075777A1 PCT/CN2017/108519 CN2017108519W WO2019075777A1 WO 2019075777 A1 WO2019075777 A1 WO 2019075777A1 CN 2017108519 W CN2017108519 W CN 2017108519W WO 2019075777 A1 WO2019075777 A1 WO 2019075777A1
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impeller
blade
blades
long
inlet
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PCT/CN2017/108519
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English (en)
French (fr)
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董亮
潘琦
代翠
刘厚林
谈明高
王勇
王凯
吴贤芳
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江苏大学
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Priority to US16/755,153 priority Critical patent/US20210192103A1/en
Publication of WO2019075777A1 publication Critical patent/WO2019075777A1/zh

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    • G—PHYSICS
    • G06—COMPUTING; CALCULATING OR COUNTING
    • G06F—ELECTRIC DIGITAL DATA PROCESSING
    • G06F30/00—Computer-aided design [CAD]
    • G06F30/20—Design optimisation, verification or simulation
    • G06F30/28—Design optimisation, verification or simulation using fluid dynamics, e.g. using Navier-Stokes equations or computational fluid dynamics [CFD]
    • 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
    • F04D29/22—Rotors specially for centrifugal pumps
    • F04D29/24—Vanes
    • 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
    • F04D29/22—Rotors specially for centrifugal pumps
    • F04D29/2205—Conventional flow pattern
    • F04D29/2216—Shape, geometry
    • 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
    • F04D29/22—Rotors specially for centrifugal pumps
    • F04D29/24—Vanes
    • F04D29/242—Geometry, shape
    • 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
    • F04D29/22—Rotors specially for centrifugal pumps
    • F04D29/24—Vanes
    • F04D29/242—Geometry, shape
    • F04D29/245—Geometry, shape for special effects
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D9/00—Priming; Preventing vapour lock
    • F04D9/02—Self-priming pumps
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D9/00—Priming; Preventing vapour lock
    • F04D9/004—Priming of not self-priming pumps
    • G—PHYSICS
    • G06—COMPUTING; CALCULATING OR COUNTING
    • G06F—ELECTRIC DIGITAL DATA PROCESSING
    • G06F2111/00—Details relating to CAD techniques
    • G06F2111/10—Numerical modelling

Definitions

  • the invention belongs to the field of centrifugal pump research, and particularly relates to an optimized design method of a jet self-priming centrifugal pump.
  • the present invention relates to impeller inlet optimization, tilting optimization of the front and rear cover of the impeller, and design of the splitter vanes between the long blades.
  • the pump As a general-purpose machine, the pump is mainly used to convert the mechanical energy of the prime mover into the energy of the liquid. It has a wide variety of applications and has been widely used in various sectors of the national economy and in high-tech fields such as aerospace vessels. According to statistics, the power consumption of the pump accounts for 18% of the total power generation, so the energy saving potential is huge.
  • the dead center head is also considered.
  • the invention improves the efficiency of the jet self-priming centrifugal pump by optimizing the impeller inlet and the cover structure, and proposes a long and short blade design. The method improves the shut-off head of the pump when the outer diameter of the impeller is constant.
  • the patent application related to the present invention includes: "A composite variable curvature low-speed rotational speed rational pump impeller design method", the invention of the use of the splitter blade in the publication number CN103994099A, their invention in the splitter blade
  • the inclination angle was designed so that the inclination angle was in the range of (18° to 24°), and the blade wrap angle was in the range of (70° to 82°).
  • the invention selects the blade pitch angle and the wrap angle parameters by a fixed range of angles.
  • the invention titled “Xing Shubing, Zhu Rongsheng, Yang Ailing, etc.” is “Design Method for a Swirl Pump with Long and Short Blades”, publication number CN103541925A.
  • the design of the splitter vane for the swirl pump is to improve the efficiency of the swirl pump.
  • the present invention differs from the related patents in that the present invention employs a splitter blade inlet diameter, a splitter blade length, a splitter blade circumferential position bias, and a tilt angle for the splitter blade in selecting the geometrical parameters of the splitter blade.
  • the parameters are designed.
  • the invention adopts the quantitative relationship between the splitter blade and the long blade to establish the geometric parameter to determine the parameter range of the splitter blade, so that the gain effect of the splitter blade is optimized.
  • the present invention proposes a design method for optimizing the pump inlet and the front and rear cover plates, and the related art similar to the present invention is not found by searching.
  • the invention improves the performance of the original jet self-priming centrifugal pump, and achieves the goal of improving the lift, increasing the flow rate, and reducing the noise.
  • the object of the present invention is to provide a jet type self-priming method for the above-mentioned jet self-priming centrifugal pump, which has a large inlet loss, a disc friction loss, an impeller outer diameter D 2 fixed, and a lift head lift cannot be improved, and the noise is large.
  • Optimized design method for suction centrifugal pump Cutting at the impeller inlet, tilting of the front and rear covers, and optimized design of the splitter vanes.
  • the invention provides two sides of the inlet side, namely the cutting length a, b of the vertical side and the horizontal side, the inclined position diameter D t of the front and rear cover plates, and the thickness of the front cover and the rear cover wall thickness at the impeller exit after the optimization of the inclination ⁇ 1 .
  • Set the number of long blades Z 1 after the splitter blades, the angle ⁇ 1 of the optimized long blades, the inlet diameter D si of the split blades, the arc length S 2 of the split blades, the circumferential bias of the split blades ⁇ 1 , the inclination of the split blades The angle ⁇ 2 and the parameter selection and optimization method of the thickness of the splitter blade.
  • the invention is simple to implement and can effectively improve the performance of the jet self-priming centrifugal pump.
  • the technical scheme of the present invention is: an optimized design method of a jet self-priming centrifugal pump, including optimizing an impeller blade;
  • the optimization of the impeller blades is to provide a splitter blade between the long blades of the pump, including the selection of the number of blades Z, the optimized long blade wrap angle ⁇ 1 , the inlet diameter D si of the splitter blade, and the split blade arc length S 2 , the splitter blade offset angle ⁇ 1 to the long blade suction surface, and the splitter blade tilt angle ⁇ 2 ;
  • the splitter blade arc length S 2 and the long blade arc length S 1 must conform to the following relationship:
  • the splitter blade inclination angle ⁇ 2 and the long blade pitch angle ⁇ 1 parameters are in accordance with the following relationship:
  • the thickness of the inlet and outlet of the splitter blade is selected to be consistent with the thickness of the long blade inlet and outlet.
  • the impeller inlet side of the impeller inlet is cut, the vertical side cutting length is a, and the vertical side cutting length a and the impeller hub diameter d h parameters are in accordance with the following relationship:
  • the impeller inlet side of the impeller inlet is cut, the horizontal side cutting length is b, and the horizontal side cutting length b and the impeller hub diameter d h parameters are in accordance with the following relationship:
  • the above solution further includes tilting the front cover of the impeller and the rear cover of the impeller;
  • the tilting design of the impeller front cover and the impeller rear cover includes a design for the inclined position diameter D t ;
  • the tilting design of the impeller front cover and the impeller rear cover further includes a thickness ⁇ 1 design of the impeller front cover and the impeller rear cover at the impeller exit after the tilt optimization;
  • the thickness of the impeller front cover plate and the impeller rear cover wall thickness ⁇ 1 at the impeller outlet and the wall thickness thickness ⁇ 2 parameters of the impeller front cover plate and the impeller rear cover plate are optimized as follows:
  • K 4 is the correction factor
  • k 4 (0.6 to 0.9).
  • the number of long blades Z 2 on the optimized pump is rounded up by the correction coefficient Z' and the calculated result of the long blade number Z 1 of the original pump.
  • the number of long blades Z 2 on the optimized pump is equal to the number Z 3 of the split blades.
  • the present invention improves the performance of the pump by adding a splitter vane between the long blades of the pump, thereby improving the efficiency of the pump and increasing the gain effect of the lift of the pump.
  • the invention optimizes the impeller inlet, and when the liquid passes through the inlet side of the impeller, an impact is generated, thereby generating an impact loss.
  • the present invention cuts the inlet side of the impeller into a buffer zone. In this way, the loss of the liquid flowing through it is much smaller, and the effect of reducing the impact loss of the inlet can be well achieved.
  • the present invention optimizes the tilting of the front cover and the rear cover to reduce the friction loss of the disk at the front cover and the rear cover of the impeller without changing the outer diameter of the impeller.
  • the impeller hydraulic optimization on the current self-priming centrifugal pump with rated power of 800w is realized.
  • FIG. 1 is a perspective view of an impeller shaft and an enlarged view of an impeller inlet, in accordance with an embodiment of the present invention.
  • FIG. 2 is a schematic diagram of an impeller water original model according to an embodiment of the present invention.
  • FIG. 3 is a model diagram of an optimized impeller water level according to an embodiment of the present invention.
  • Figure 4 is a graph showing the performance of the original pump of one embodiment of the present invention.
  • Figure 5 is an optimized performance curve for one embodiment of the present invention.
  • the invention provides an optimized design method of a jet self-priming centrifugal pump, which comprises optimizing an impeller inlet 1, an impeller front cover plate 2, an impeller rear cover plate 3 and an impeller blade.
  • the impeller inlet is optimized to generate an impact when the liquid passes through the inlet side of the impeller, thereby generating an impact loss.
  • the present invention cuts the inlet side of the impeller into a buffer zone, so that the liquid flows through the The loss at the time is much smaller, and the effect of reducing the impact loss of the inlet can be achieved very well.
  • the cutting scheme employed in the present invention is:
  • the inlet side On the two sides of the inlet side, that is, the vertical side and the horizontal side, respectively, the appropriate length is selected, the length selected on the vertical side is expressed by a, and the length selected on the horizontal side is represented by b, and the present invention passes a, b and
  • the quantitative relationship of the hub diameter to determine the value of a, b, the expression is as follows:
  • K 1 - correction factor (0.01 ⁇ 0.05)
  • K 2 (0.02 ⁇ 0.08)
  • the value of a, b can be determined by the correction factor K 1 , K 2 under the condition that the hub diameter d h is known.
  • the invention optimizes the tilt design of the front cover plate and the rear cover plate, thereby reducing the friction loss of the disk at the front cover plate and the rear cover plate of the impeller without changing the outer diameter of the impeller.
  • the present invention first determines the tilt position diameter D t , and then determines the thickness ⁇ 1 of the front and rear cover wall thickness at the impeller exit after the tilt optimization, when these two parameters are determined.
  • the tilting design of the front cover and the rear cover is completed.
  • the present invention establishes a quantitative relationship with the outer diameter D 2 of the impeller, the relationship is as follows:
  • K 3 - correction factor, K 3 (0.75 ⁇ 0.95)
  • the inclination position diameter D t can be determined by the correction coefficient K 3 .
  • the present invention adopts the tilt-optimized rear cover and the rear cover wall thickness ⁇ 1 at the impeller exit and before optimization
  • the wall thickness ⁇ 2 of the cover and the rear cover establishes a quantitative relationship, and the expression is as follows:
  • the impeller blades are optimized such that the impeller blades are optimized by providing a splitter blade (4) between the long blades of the pump, including the selection of the number of blades Z, the optimized long blade wrap angle ⁇ 1 , and the splitter blades
  • the inlet diameter D si , the split blade arc length S 2 , the split vane to the long vane suction surface offset angle ⁇ 1 , and the split vane tilt angle ⁇ 2 the optimized design of the split vane inlet and outlet thickness.
  • the design method of setting the splitter vanes 4 between the long blades is adopted to increase the dead center lift and at the same time reduce the blockage of the impeller inlet.
  • the specific methods are as follows:
  • the optimized pump length number Z 2 is used to establish a quantitative relationship with the number of long blades Z 1 of the original pump to determine the number of optimized pump lengths Z 2 .
  • the established expression is as follows:
  • the present invention adopts the optimized long blade wrap angle ⁇ 1 and the wrap angle ⁇ of the original pump long blade, the number of long blades of the original pump Z 1 , and the optimized pump
  • the long blade number Z 2 establishes a quantitative relationship, and the relationship is as follows:
  • Splitter blade inlet diameter D si is directly related to the length of the splitter blade, in theory, the longer the splitter blade, the smaller the D si, corresponding to the larger head.
  • the splitter blade is too long, it will block the impeller inlet, and the increase of the lift will be less, which will cause the efficiency to decrease.
  • the shunt blades are too short to improve the impeller exit jet-wake structure and to improve pump efficiency.
  • the inlet diameter D si of the splitter blade the quantitative relationship between the inlet diameter D si of the splitter blade and the outer diameter D 2 of the impeller is proposed. The relationship is as follows:
  • D 2 under certain circumstances can be determined splitter blade inlet diameter D si through D ⁇ .
  • the splitter blade When the splitter blade is provided an arc length parameter S 2, it provides a quantitative relationship between the arc length of the blade shunt S 2 and the arc length S of the long blade. 1, the relationship is as follows:
  • K 5 (0.4 ⁇ 0.8)
  • the required splitter blade arc length S 2 can be obtained by the correction factor K 5 .
  • the present invention defines the angle between the adjacent two long blades as ⁇ , and defines the angle of the offset of the split blades to the long blade suction surface as ⁇ 1 , and the present invention passes ⁇ and ⁇ 1
  • the ratio is calculated as follows:
  • K 6 (0.4 ⁇ 0.6)
  • the magnitude of ⁇ 1 can be determined by the correction coefficient K 6 to determine the circumferential offset position of the splitter blade.
  • the diverting blade inclination angle ⁇ 2 can determine the inclination position of the diverting blade, and establish a quantitative relationship by the diverging blade inclination angle ⁇ 2 and the long blade inclination angle ⁇ 1 parameter, and the relationship is as follows:
  • K 7 (0.5 ⁇ 0.9)
  • the invention also provides the thickness of the inlet and outlet of the splitter blade, and the thickness of the inlet and outlet of the splitter blade of the present invention is consistent with the thickness of the inlet and outlet of the long blade.
  • the thickness ⁇ 1 1.5 mm.
  • the inlet diameter Dsi of the splitter blade As shown in FIG. 3, in the parameter determination of the inlet diameter Dsi of the splitter blade, it is calculated by the formula 7.
  • the long blade arc length S 1 64 mm
  • the long blade inclination angle ⁇ 1 55°
  • the embodiment adopts parameters in which the short blade thickness is consistent with the long blade thickness.
  • the short blade inlet thickness is 3 mm
  • the outlet thickness is 7 mm
  • the intermediate thickness is 5 mm.
  • Figure 4 is the performance curve of the original 800w jet self-priming centrifugal pump.
  • Figure 5 is the performance curve of the pump after optimization design. After comparison of the two figures, it can be clearly seen that after the above impeller water optimization The flow-head curve is steeply lowered, so that the efficiency of the pump is improved without exceeding the rated power, and the lift is also obviously improved.
  • the impeller hydraulic optimization on the current self-priming centrifugal pump with rated power of 800w is realized.

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Abstract

为了解决进口冲击损失、圆盘摩擦损失、叶轮外径固定情况下关死点扬程无法提高的问题，提供一种射流式自吸离心泵的优化设计方法，是一种在叶轮进口（1）处切削、前盖板（2）和后盖板（3）设置倾斜、以及分流叶片（4）的优化设计方法。其给出了进口边两边，即竖直边与水平边的切削长度a，b，前后盖板（2，3）的倾斜位置直径Dt，倾斜优化后叶轮出口处前盖板（2）和后盖板（3）壁厚厚度δ1，设置分流叶片（4）后长叶片数Z1，优化后长叶片包角Φ1，分流叶片（4）的进口直径Dsi，分流叶片（4）圆弧长度S2，分流叶片（4）轴向偏置度θ1，分流叶片（4）倾斜角α2，以及分流叶片（4）的厚度参数选择和优化方法。该方法实施简单，且能够有效地提高射流式自吸离心泵的性能。

Description

一种射流式自吸离心泵的优化设计方法 技术领域
本发明属于离心泵研究领域，具体涉及一种射流式自吸离心泵的优化设计方法。具体的说，本发明涉及叶轮进口优化，叶轮前后盖板倾斜优化设置，以及长叶片间设置分流叶片的设计方法。
背景技术
泵作为一种通用机械，主要用于把原动机的机械能转换为液体的能量，其种类繁多，在国民经济各部门以及航天船舶等高科技领域都得到了广泛的应用。据统计，泵的耗电量占总发电量的18％，因此节能潜力巨大。对于射流式自吸离心泵而言，除了效率外还要考虑关死点扬程，本发明通过优化叶轮进口及盖板结构来提高射流式自吸离心泵的效率，并提出一种长短叶片的设计方法在叶轮外径不变的情况下提高泵的关死点扬程。
经检索，与本发明相关的专利申请有：《一种复合式变曲率低比转速理性泵叶轮设计方法》，公开号：CN103994099A的中就用到分流叶片的发明，他们的发明中对分流叶片倾斜角度做了设计，倾斜角度在(18°～24°)的范围内，叶片包角在(70°～82°)的范围内。该发明通过一个固定的角度范围来选择叶片倾斜角以及包角的参数。此外，由邢树兵、朱荣生、杨爱玲等发表的发明名称为《一种长短叶片的旋流泵设计方法》，公开号CN103541925A，对旋流泵做了分流叶片的设计，来提高旋流泵的效率。
本发明与现相关专利的有不同之处在于对分流叶片的几何参数的选择上，本发明采用分流叶片进口直径，分流叶片长度，分流叶片周向位置偏置度，以及对于分流叶片的倾斜角参数进行设计。本发明采用分流叶片与长叶片之间建立几何参数的量化关系来确定分流叶片的参数范围，从而使得分流叶片的增益效果达到最佳。此外，本发明为了进一步降低泵进口损失以及圆盘摩擦损失，提出了一种泵进口与前后盖板优化的设计方法，通过检索未见与本发明相似的相关技术。本发明通过对上述的几何参数进行设计从而使得原有射流式自吸离心泵的性能的提高，达到提高扬程，加大流量，降低噪声的目标。
发明内容
本发明的目的是针对上述射流式自吸离心泵上存在进口损失大，圆盘摩擦损失、叶轮外径D2固定了以后关死点扬程无法提高，噪声大等问题，提供一种射流式自吸离心泵的优化设计方法。在叶轮进口处切削、前盖板和后盖板设置倾斜、以及分流叶片的优化 设计。本发明给出了进口边两边，即竖直边与水平边的切削长度a，b，前后盖板的倾斜位置直径Dt，倾斜优化后叶轮出口处前盖板和后盖板壁厚厚度δ1，设置分流叶片后长叶片数Z1，优化后长叶片包角Φ1，分流叶片的进口直径Dsi，分流叶片圆弧长度S2，分流叶片周向偏置度θ1，分流叶片倾斜角α2，以及分流叶片的厚度的参数选择和优化方法。本发明实施简单，且能够有效地提高射流式自吸离心泵的性能。
本发明的技术方案是：一种射流式自吸离心泵的优化设计方法，包括对叶轮叶片进行优化；
对所述叶轮叶片进行优化是在泵的长叶片之间设置分流叶片，包括对叶片数Z的选择，优化后长叶片包角Φ1，分流叶片的进口直径Dsi，分流叶片圆弧长度S2，分流叶片向长叶片吸力面偏置角度θ1，以及分流叶片倾斜角α2；
优化后泵上的长叶片数Z2与原泵的长叶片数Z1符合以下关系：
Z2＝Z`*Z1          公式五
式中：Z`是修正系数，Z`＝0.6；
优化后长叶片包角Φ1与原泵长叶片的包角Φ、原泵的长叶片数Z1、优化后泵上的长叶片数Z2要符合以下关系：
Φ1＝Z1Φ/KΦZ2     公式六
KΦ是包角系数，KΦ＝0.9426
分流叶片进口直径Dsi与叶轮外径D2参数之间要符合以下关系：
D`＝Dsi/D2         公式七
D`是修正系数，D`＝(0.4～0.8)
分流叶片圆弧长度S2与长叶片圆弧长度S1要符合以下关系：
K5＝S2/S1          公式八
K5是修正系数，K5＝(0.4～0.8)；
分流叶片向长叶片吸力面偏置角度θ1与相邻两长叶片之间的夹角θ参数要符合以下关系：
K6＝θ1/θ         公式九
K6是修正系数，K6＝(0.4～0.6)；
分流叶片倾斜角α2与长叶片倾斜角α1参数要符合以下关系：
K7＝α2/α1        公式十
K7是修正系数，K7＝(0.5～0.9)。
上述方案中，所述分流叶片进出口厚度选取与长叶片进出口厚度一致。
上述方案中，还包括对叶轮进口的叶轮进口边进行切削；
对所述叶轮进口的叶轮进口边进行切削，竖直边切削长度为a，竖直边切削长度为a与叶轮轮毂直径dh参数之间符合以下关系：
K1＝a/dh        公式一
式中：K1是修正系数，K1＝(0.01～0.05)。
进一步的，对叶轮进口的叶轮进口边进行切削，水平边切削长度为b，水平边切削长度为b与叶轮轮毂直径dh参数之间符合以下关系：
K2＝b/dh        公式二
式中：K2是修正系数，K2＝(0.02～0.08)。
上述方案中，还包括对所述叶轮前盖板和叶轮后盖板进行倾斜设计；
对所述叶轮前盖板和叶轮后盖板进行倾斜设计包括对倾斜位置直径Dt的设计；
所述叶轮前盖板和叶轮后盖板倾斜位置直径Dt与叶轮外径D2参数之间符合以下关系：
K3＝Dt/D2       公式三
式中：K3是修正系数，K3＝(0.75～0.95)。
进一步的，对所述叶轮前盖板和叶轮后盖板进行倾斜设计还包括对倾斜优化后叶轮出口处叶轮前盖板和叶轮后盖板的厚度δ1设计；
所述倾斜优化后叶轮出口处叶轮前盖板和叶轮后盖板壁厚厚度δ1与优化前叶轮前盖板和叶轮后盖板的壁厚厚度δ2参数之间符合以下关系：
K4＝δ1/δ2     公式四
式中：K4是修正系数，k4＝(0.6～0.9)。
上述方案中，所述优化后泵上的长叶片数Z2通过修正系数Z`与原泵的长叶片数Z1的计算后的结果向上取整。
进一步的，所述优化后泵上的长叶片数Z2与分流叶片数Z3相等。
与现有技术相比，本发明的有益效果：
1.本发明通过在泵的长叶片之间增添分流叶片的方法来提高泵的性能，从而提高泵的效率，提高泵的扬程的增益效果。
2.本发明对叶轮进口进行优化，当液体通过叶轮进口边的时候会产生冲击，进而产生冲击损耗，为了减小损耗，所以本发明将叶轮进口边进行切削，使其成为一个缓冲区， 这样液体流经此处时损耗就要小得多，能很好的达到减少进口冲击损失的效果。
3.本发明对前盖板、后盖板进行倾斜优化设计，从而在不改变叶轮外径的情况下减少叶轮前盖板和后盖板处的圆盘摩擦损失。
4.本发明将优化前和优化后的800w射流式自吸离心泵的性能对比，可以清楚的看到经过叶轮水利优化后，使得泵在不超过额定功率下效率得到了的提高，扬程也有了明显的提高，本发明通过几何参数优化，从而将原先泵的最大扬程提高到131.23ft，最大流量达到3600L/H，转速达到n＝2995r/m，效率提高到17.2％，噪音降低到78dB。实现在现有额定功率为800w的射流式自吸离心泵上的叶轮水力优化。
附图说明
图1是本发明的一个实施例的叶轮轴面图以及叶轮进口处切削放大图。
图2是本发明的一个实施例的叶轮水利原模型图。
图3是本发明的一个实施例的叶轮水利经过优化后的模型图。
图4是本发明的一个实施例的原来泵的性能曲线。
图5是本发明的一个实施例的经过优化后的性能曲线。
图中，1叶轮进口；2叶轮前盖板；3.叶轮后盖板；4.分流叶片；5.原泵长叶片；6.优化后泵长叶片。
具体实施方式
下面结合附图和具体实施方式对本发明作进一步详细说明，但本发明的保护范围并不限于此。
本发明所述一种射流式自吸离心泵的优化设计方法，包括对叶轮进口1、对叶轮前盖板2、叶轮后盖板3和叶轮叶片进行优化。
对叶轮进口进行优化，当液体通过叶轮进口边的时候会产生冲击，进而产生冲击损耗，为了减小损耗，所以本发明将叶轮进口边进行切削，使其成为一个缓冲区，这样液体流经此处时损耗就要小得多，能很好的达到减少进口冲击损失的效果。
为了使得叶轮进口边变成所想要的缓冲区，本发明采用的切削方案为：
在进口边的两边，即竖直边与水平边，分别选取合适的长度，在竖直边选取的长度用a来表述，在水平边选取的长度用b来表示，本发明通过a，b与轮毂直径的量化关系来确定a，b的值，表达式如下：
K1＝a/dh公式一
dh——叶轮轮毂直径，mm
K1——修正系数，K1＝(0.01～0.05)
K2＝b/dh公式二
K2——修正系数，K2＝(0.02～0.08)
在已知轮毂直径dh的条件下，通过修正系数K1，K2就能确定a，b的值。
叶轮在泵体内旋转时，由于叶轮转速快，叶轮的前盖板、后盖板外表面与液体间产生摩擦损失，这部分损失与叶轮直径大小有关，称之为圆盘摩擦损失。本发明对前盖板、后盖板进行倾斜优化设计，从而在不改变叶轮外径的情况下减少叶轮前盖板和后盖板处的圆盘摩擦损失。
对于前盖板和后盖板倾斜优化参数的设置，本发明首先确定好倾斜位置直径Dt，然后确定经过倾斜优化后叶轮出口处前后盖板壁厚厚度δ1，当这两个参数确定后，前盖板和后盖板的倾斜设计就完成了。
对于斜位置直径Dt的参数选择时，本发明采用与叶轮外径D2建立量化关系，关系如下：
K3＝Dt/D2公式三
K3——修正系数，K3＝(0.75～0.95)
在已知叶轮外径D2的情况下，能通过修正系数K3来确定倾斜位置直径Dt。
对于倾斜优化后叶轮出口处前盖板和后盖板叶轮出口处的厚度δ1参数的选择，本发明采用倾斜优化后叶轮出口处前盖板和后盖板壁厚厚度δ1与优化前前盖板和后盖板的壁厚厚度δ2建立量化关系，表达式如下：
K4＝δ1/δ2公式四
K4——修正系数，K4＝(0.6～0.9)
在已知优化前前盖板和后盖板壁厚厚度δ2的情况下，可以通过修正系数K4来确定倾斜优化后叶轮出口处前盖板和后盖板壁厚厚度δ1。
对所述叶轮叶片进行优化为：对所述叶轮叶片进行优化是在泵的长叶片之间设置分流叶片(4)，包括对叶片数Z的选择，优化后长叶片包角Φ1，分流叶片的进口直径Dsi，分流叶片圆弧长度S2，分流叶片向长叶片吸力面偏置角度θ1，以及分流叶片倾斜角α2，分流叶片进出口厚度的优化设计。
采用长叶片间设置分流叶片4的设计方法来增加关死点扬程，同时来减少叶轮进口的堵塞，具体采用的方法如下：
随着叶轮叶片数Z的增加，扬程增加很明显，但叶片数过多会产生大量的水力摩擦 损失，反而降低了泵的效率，所以在选取合适的叶片数Z尤为重要，同时叶片数的增加会导致功率增加，易出现超功率。为了在不改变叶轮外径D2和不超功率的情况下，提出了一种添加分流叶片的方式。
采用优化后泵长叶片数Z2与原泵的长叶片数Z1建立量化关系，以确定优化后泵长叶片数Z2，建立的表达式如下：
Z2＝Z`*Z1公式五
Z`——修正系数，Z`＝0.6
优化后泵上的长叶片数Z2通过修正系数与原泵的叶片数Z1的计算后的结果向上取整，确定优化后泵上的长叶片数Z2后，而分流叶片的叶片数Z3与优化后泵上的长叶片数Z2相等(即Z2＝Z3)。
采用分流叶片的设计后，为了确定长叶片包角Φ1，本发明采用优化后长叶片包角Φ1与原泵长叶片的包角Φ、原泵的长叶片数Z1、优化后泵上的长叶片数Z2建立量化关系，关系式如下：
Φ1＝Z1Φ/KΦZ2公式六
KΦ——包角系数，KΦ＝0.926
通过上述关系，在已知原长叶片包角Φ，原泵叶片数Z1后，通过叶片系数Z`算得的优化后泵上的长叶片数Z2一系列相关参数后就可以确定优化后长叶片包角Φ1的值。
分流叶片进口直径Dsi直接关系到分流叶片的长度，从理论上讲，分流叶片越长，Dsi越小，对应着越大的扬程。但从前期研究可看出，分流叶片太长会堵塞叶轮进口，扬程的增加较少，反而会引起效率的降低。然而，分流叶片太短起不到改善叶轮出口射流-尾迹结构，以及提高水泵效率的作用。在对分流叶片进口直径Dsi的参数设置上，提出了分流叶片进口直径Dsi与叶轮外径D2的量化关系，关系式如下：
D`＝Dsi/D2公式七
D`——修正系数，D`＝(0.4～0.8)
在D2一定的情况下就能通过D`来确定分流叶片进口直径Dsi。
在设置分流叶片圆弧长度S2的参数时，提出一种分流叶片圆弧长度S2与长叶片圆弧长度S1的量化关系，关系式如下：
K5＝S2/S1公式八
K5——修正系数，K5＝(0.4～0.8)
在已知长叶片圆弧长度S1的情况下，通过修正系数K5就能得出所需要的分流叶片圆 弧长度S2。
由离心叶轮内的流动滑移理论可知，叶轮流道内速度分布在周向分布不均匀，因而分流叶片不能布置在流道正中间，需要向叶片背面偏置，有利于改善叶轮出口的“射流-尾迹”结构，提高水泵性能。在短叶片的周向位置确定上，本发明把相邻两长叶片之间的夹角定义为θ，把分流叶片向长叶片吸力面偏置角度定义为θ1，本发明通过θ与θ1进行比值，关系式如下：
K6＝θ1/θ公式九
K6——修正系数，K6＝(0.4～0.6)
在已知相邻两长叶片之间的夹角θ在条件下，就能通过修正系数K6来确定θ1的大小，从而确定分流叶片的周向偏置位置。
分流叶片倾斜角α2能确定分流叶片的倾斜位置，通过分流叶片倾斜角α2与长叶片倾斜角α1参数建立量化关系，关系式如下：
K7＝α2/α1       公式十
K7——修正系数，K7＝(0.5～0.9)
本发明还对分流叶片进出口厚度进行设置，本发明分流叶片进出口厚度选取与长叶片进出口厚度是一致的。
下面以一台射流式自吸低比转速离心泵为例来阐述本发明的实施过程。该泵的具体参数如下：额定功率为800w，比转速为32.0，扬程H＝121.39ft，流量Q＝3700L/H，转速n＝2775r/m，效率η＝14.3％，叶轮外径D2＝117mm，出口宽度b2＝4mm，包角Φ＝100°，进口角β1＝19.3°，出口角β2＝35.0°，轮毂直径dh＝19mm，叶片数Z＝6，叶轮前后盖板厚度δ2＝2mm。
如附图1所示，液体进入叶轮进口1的叶轮进口边时会产生冲击损失，本发明在叶轮进口边的两边，即竖直边与水平边，分边选取合适长度进行切削，使得叶轮进口边切削成一个缓冲区，叶轮进口边的竖直边切削长度为a，水平边切削长度为b，由叶轮轮毂直径dh＝19.2mm，通过公式一和公式二可以算出a，b的值，本设计通过CFD数值计算后选择k1＝0.02，k2＝0.03，计算得出a＝0.4mm，b＝0.6mm。
如附图1所示，是本发明对叶轮前盖板2和叶轮后盖板3进行倾斜优化设计，图1中的叶轮外径D2＝117mm，通过CFD数值计算本设计选用修正系数K3＝0.932，从而根据公式三计算得到倾斜位置直径Dt＝109mm。
如附图1所示，叶轮前后盖板壁厚厚度δ2＝2mm，经过CFD数值计算本设计选择修 正系数K4＝0.75，从而根据公式四可以计算得到优化后叶轮出口处前后盖板壁厚厚度δ1＝1.5mm。
如附图2所示，本实施例中原泵的长叶片数Z1＝6，如附图3所示，是本发明对长、短叶片优化设计的方案，通过公式五计算得出优化后泵上的长叶片数Z2＝4，计算出的叶片数向上取整，进而分流叶片数Z3＝4。
如附图2所示，本实施例中原泵长叶片5的包角Φ＝100°，原泵的叶片数Z1＝6，根据上述公式六计算得到优化后泵上的长叶片数Z2＝4，通过公式六可以计算得到优化后长叶片6的包角Φ1＝162°，如附图3所示。
由附图3所示，在对分流叶片的进口直径Dsi的参数确定上，通过公式七来计算得到，本实施例叶轮外径D2＝117mm，通过CFD数值计算选取修正系数D`＝0.72，从而可以得到分流叶片进口直径Dsi＝84.2mm。
由附图3所示，长叶片圆弧长度S1＝64mm，通过CFD数值计算，选择修正系数K5＝0.6，通过公式八计算可以得到分流叶片圆弧长度S2＝38.5mm。
由附图3所示，相邻两长叶片之间的夹角θ＝72°，通过CFD数值计算，本实施例选取修正系数K6＝0.4，这样就可以通过公式九得到分流叶片向长叶片吸力面偏置角度θ1＝28.8°。
如附图3所示，本实施例长叶片倾斜角α1＝55°，通过CFD数值计算，本实施例选取修正系数K7＝0.8，从而根据公式十计算得到分流叶片倾斜角α2＝44°。
在对短叶片厚度进行设置时，本实施例采取短叶片厚度与长叶片厚度一致的参数，本实施例短叶片进口厚度为3mm，出口厚度为7mm，中间厚度为5mm。
如附图4，是原来800w射流式自吸离心泵的性能曲线图，附图5是经过优化设计后泵的性能曲线图，经过两图的对比，可以清楚的看到经过上述叶轮水利优化后，流量-扬程曲线陡降，从而使得泵在不超过额定功率下效率得到了的提高，扬程也有了明显的提高，本发明实施例通过上述的几何参数优化，从而将原先泵的最大扬程提高到131.23ft，最大流量达到3600L/H，转速达到n＝2995r/m，效率提高到17.2％，噪音降低到78dB。实现在现有额定功率为800w的射流式自吸离心泵上的叶轮水力优化。
上文所列出的一系列的详细说明仅仅是针对本发明的可行性实施例的具体说明，它们并非用以限制本发明的保护范围，凡未脱离本发明技艺精神所作的等效实施例或变更均应包含在本发明的保护范围之内。

Claims (8)

  1. 一种射流式自吸离心泵的优化设计方法，其特征在于，包括对叶轮叶片进行优化；
    对所述叶轮叶片进行优化是在泵的长叶片之间设置分流叶片(4)，包括对叶片数Z的选择，优化后长叶片包角Φ1，分流叶片的进口直径Dsi，分流叶片圆弧长度S2，分流叶片向长叶片吸力面偏置角度θ1，以及分流叶片倾斜角α2；
    优化后泵上的长叶片数Z2与原泵的长叶片数Z1符合以下关系：
    Z2＝Z`*Z1    公式五
    式中：Z`是修正系数，Z`＝0.6；
    优化后长叶片包角Φ1与原泵长叶片的包角Φ、原泵的长叶片数Z1、优化后泵上的长叶片数Z2要符合以下关系：
    Φ1＝Z1Φ/KΦZ2    公式六
    KΦ是包角系数，KΦ＝0.9426
    分流叶片进口直径Dsi与叶轮外径D2参数之间要符合以下关系：
    D`＝Dsi/D2    公式七
    D`是修正系数，D`＝(0.4～0.8)
    分流叶片圆弧长度S2与长叶片圆弧长度S1要符合以下关系：
    K5＝S2/S1    公式八
    K5是修正系数，K5＝(0.4～0.8)；
    分流叶片向长叶片吸力面偏置角度θ1与相邻两长叶片之间的夹角θ参数要符合以下关系：
    K6＝θ1/θ    公式九
    K6是修正系数，K6＝(0.4～0.6)；
    分流叶片倾斜角α2与长叶片倾斜角α1参数要符合以下关系：
    K7＝α2/α1    公式十
    K7是修正系数，K7＝(0.5～0.9)。
  2. 根据权利要求1所述射流式自吸离心泵的优化设计方法，其特征在于，所述分流叶片进出口厚度选取与长叶片进出口厚度一致。
  3. 根据权利要求1所述射流式自吸离心泵的优化设计方法，其特征在于，还包括对叶轮进口(1)的叶轮进口边进行切削；
    对所述叶轮进口(1)的叶轮进口边进行切削，竖直边切削长度为a，竖直边切削长 度为a与叶轮轮毂直径dh参数之间符合以下关系：
    K1＝a/dh    公式一
    式中：K1是修正系数，K1＝(0.01～0.05)。
  4. 根据权利要求3所述射流式自吸离心泵的优化设计方法，其特征在于，对叶轮进口(1)的叶轮进口边进行切削，水平边切削长度为b，水平边切削长度为b与叶轮轮毂直径dh参数之间符合以下关系：
    K2＝b/dh    公式二
    式中：K2是修正系数，K2＝(0.02～0.08)。
  5. 根据权利要求1所述射流式自吸离心泵的优化设计方法，其特征在于，还包括对所述叶轮前盖板(2)和叶轮后盖板(3)进行倾斜设计；
    对所述叶轮前盖板(2)和叶轮后盖板(3)进行倾斜设计包括对倾斜位置直径Dt的设计；
    所述叶轮前盖板(2)和叶轮后盖板(3)倾斜位置直径Dt与叶轮外径D2参数之间符合以下关系：
    K3＝Dt/D2    公式三
    式中：K3是修正系数，K3＝(0.75～0.95)。
  6. 根据权利要求5所述射流式自吸离心泵的优化设计方法，其特征在于，对所述叶轮前盖板(2)和叶轮后盖板(3)进行倾斜设计还包括对倾斜优化后叶轮出口处叶轮前盖板(2)和叶轮后盖板(3)的厚度δ1设计；
    所述倾斜优化后叶轮出口处叶轮前盖板(2)和叶轮后盖板(3)壁厚厚度δ1与优化前叶轮前盖板和叶轮后盖板的壁厚厚度δ2参数之间符合以下关系：
    K4＝δ1/δ2    公式四
    式中：K4是修正系数，k4＝(0.6～0.9)。
  7. 根据权利要求1所述射流式自吸离心泵的优化设计方法，其特征在于，所述优化后泵上的长叶片数Z2通过修正系数Z`与原泵的长叶片数Z1的计算后的结果向上取整。
  8. 根据权利要求7所述射流式自吸离心泵的优化设计方法，其特征在于，所述优化后泵上的长叶片数Z2与分流叶片数Z3相等。
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