WO2020042212A1 - 一种基于耦合仿生优化的叶片泵叶轮 - Google Patents

一种基于耦合仿生优化的叶片泵叶轮 Download PDF

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Publication number
WO2020042212A1
WO2020042212A1 PCT/CN2018/104541 CN2018104541W WO2020042212A1 WO 2020042212 A1 WO2020042212 A1 WO 2020042212A1 CN 2018104541 W CN2018104541 W CN 2018104541W WO 2020042212 A1 WO2020042212 A1 WO 2020042212A1
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Prior art keywords
blade
cover plate
shaped groove
vane pump
pump impeller
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PCT/CN2018/104541
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English (en)
French (fr)
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代翠
董亮
陈怡平
王照雪
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江苏大学
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Publication of WO2020042212A1 publication Critical patent/WO2020042212A1/zh

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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
    • F04D29/22—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
    • F04D29/2261—Rotors specially for centrifugal pumps with special measures
    • F04D29/2272—Rotors specially for centrifugal pumps with special measures for influencing flow or boundary layer
    • 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

Definitions

  • the invention relates to the field of vane pump bionic drag reduction, in particular to a vane pump impeller based on coupled bionic optimization.
  • bionic blade of twin-turbine torque converter guide wheel smoothing the outer contour of the guide wheel blade from the blade leading edge, pressure surface contour, suction surface contour and blade tail Connected to make a dolphin shape.
  • the bionic blade of the dual-turbine torque converter guide wheel of the invention overcomes factors such as the enlargement of the leading edge of the dual-turbine torque converter guide wheel blade, the discontinuous curvature of the edge curve, and the unreasonable middle streamline in the prior art.
  • the bionic blades of the guide wheel of the dual-turbine torque converter Due to the large energy loss caused by the flow of fluid flowing through the guide wheel, the bionic blades of the guide wheel of the dual-turbine torque converter have excessively smooth and flat curves, simple structure, easy manufacture, and can effectively improve the dual-turbine torque converter. Performance.
  • the present invention provides a vane pump impeller based on coupled bionic optimization to improve the drag reduction effect of the pump.
  • the present invention achieves the above technical objectives through the following technical means.
  • a vane pump impeller based on coupling bionic optimization includes a front cover plate, a rear cover plate, and a blade.
  • a working surface of the blade is provided with a plurality of first V-shaped grooves parallel to each other at an outlet of the impeller.
  • the V-shaped groove extends from the blade exit edge to the blade inlet edge.
  • the length Lg of the first V-shaped groove is a quarter of the entire blade length.
  • the guide of the first V-shaped groove and the blade outlet edge The included angle ⁇ 1 is 95 °;
  • a plurality of mutually parallel second V-shaped grooves are provided on the back surface of the blade at the impeller exit.
  • the second V-shaped grooves extend from the blade exit edge to the blade inlet edge.
  • the length L b is one third of the length of the entire blade, and the angle ⁇ 2 between the guide of the second V-shaped groove and the exit side of the blade is 85 °;
  • the front cover plate and the rear cover plate are each provided with an array of pits.
  • Each row of pits includes a plurality of pits that are evenly spaced along the direction of the blade flow line.
  • the multiple rows of pits make the impeller flow passages equally divided into multiple
  • each row of pits includes a plurality of pits that are evenly spaced in the circumferential direction with the center line of the impeller as the center.
  • the dimples are oval dimples, and the long axis of the oval dimples is provided along the blade streamline direction.
  • the oval recesses on the front cover plate and the rear cover plate are symmetrical to each other with respect to a center plane between the front cover plate and the rear cover plate.
  • the major axis length of the oval dimple is 2 mm and the minor axis length is 1.5 mm.
  • the depth of the oval recess is h
  • the thickness of the front cover is B 1
  • the thickness of the rear cover is B 2
  • h (B 1 + B 2 ) / 20.
  • the distribution range of each row of pits from the exit edge of the impeller to the entrance edge of the blade is 0.5D 2 to 1.0D 2 , where D 2 is the diameter of the impeller outlet.
  • the number of columns in the pit array is 10 columns.
  • the depths of the first V-shaped groove and the second V-shaped groove are both h, where h is one sixth of the blade thickness ⁇ . If the blade is a non-equal thickness blade, the blade thickness ⁇ takes the maximum thickness .
  • the widths of the first V-shaped groove and the second V-shaped groove are both S, where S is one-twentieth of the width b 2 of the exit edge of the blade.
  • a plurality of the first V-shaped grooves form a first V-shaped groove group, and the distance between the first V-shaped groove group and the front cover plate and the rear cover plate is ten times the width of the blade exit edge b 2
  • a plurality of the second V-shaped grooves form a second V-shaped groove group, and the distance between the second V-shaped groove group and the front cover plate and the rear cover plate is the width of the blade exit edge width b 2 one tenth.
  • bionic optimization is performed by opening first and second V-shaped groove groups on the working surface and the back surface of the blade, respectively, and setting multiple rows by multiple rows of pits on the opposite wall surfaces of the front cover plate and the rear cover plate.
  • Bionic optimization while quantifying the length of the first and second V-grooves and the angle between the guide of the first and second V-grooves and the blade exit side, the first and second V-grooves reduce the Generated to control the boundary layer and reduce the velocity of the bottom layer of the boundary layer, that is, to reduce the binding force between the blade surface and the water, thereby reducing the frictional shear stress;
  • the pits change the fluid structure of the front and back cover layer boundary layers to suppress and delay the occurrence of turbulence , Thereby effectively reducing the resistance of the cover surface;
  • elliptical dimples are arranged along the streamline direction on the front and rear cover plates. Compared with circular dimples, the oval dimples are arranged along the streamline direction, which is more suitable for the flow of fluid on the front and rear cover plates.
  • the turbulence structure is more turbulent, so the drag reduction effect is better.
  • FIG. 1 is a schematic structural diagram of a vane pump impeller based on coupled bionic optimization according to the present invention.
  • FIG. 2 is a schematic structural diagram of a first V-shaped groove group on a working surface of a blade according to the present invention.
  • FIG. 3 is a schematic structural diagram of a second V-shaped groove group on the back surface of the blade according to the present invention.
  • FIG. 4 is a schematic structural diagram of a first V-shaped groove according to the present invention.
  • FIG. 5 is a schematic diagram of a recess on a front cover or a rear cover according to the present invention.
  • a vane pump impeller based on coupled bionic optimization includes a front cover 1, a rear cover 3, and a blade 4.
  • the working surface of the blade 4 is provided with a plurality of first V-shaped grooves 5 parallel to each other at the impeller exit.
  • the first V-shaped groove 5 extends from the blade exit edge 2 to the blade inlet edge.
  • the numerical analysis of the shear force distribution on the working surface boundary layer of the blade 4, the length Lg of the first V-shaped groove 5 is a quarter of the length of the entire blade 4, and the guidance of the first V-shaped groove 5 and the exit edge 2 of the blade
  • the included angle ⁇ 1 is 95 °, and the distance between two adjacent first V-shaped grooves 5 is 0.
  • a plurality of first V-shaped grooves 5 form a first V-shaped groove group, and the first V-shaped groove group and the front cover The distance between the plate 1 and the rear cover 3 is one-tenth of the width b 2 of the blade exit edge 2.
  • a plurality of mutually parallel second V-shaped grooves 6 are provided on the back surface of the blade 4 at the impeller exit.
  • the second V-shaped grooves 6 extend from the blade exit edge 2 to the blade inlet edge, based on the value.
  • the length L b of the second V-shaped groove 6 is one third of the length of the entire blade 4, and the angle between the guidance of the second V-shaped groove 6 and the blade exit edge 2 ⁇ 2 is 85 °, the distance between two adjacent second V-shaped grooves 6 is 0, a plurality of second V-shaped grooves 6 form a second V-shaped groove group, and the second V-shaped groove group and the front cover plate 1 The distance from the rear cover 3 is one-tenth of the width b 2 of the blade exit side 2.
  • the first V-shaped groove 5 and the second V-shaped groove 6 control the boundary layer by reducing the generation of turbulence, and reduce the velocity of the bottom layer of the boundary layer, that is, reduce the binding force between the surface of the blade 4 and water to reduce the frictional shear stress.
  • the depths of the first V-shaped groove 5 and the second V-shaped groove 6 are both h, where h is one-sixth of the thickness ⁇ of the blade 4.
  • the thickness ⁇ takes the maximum value of its thickness.
  • the widths of the first V-shaped groove 5 and the second V-shaped groove 6 are both S, where S is one-twentieth of the width b 2 of the blade exit side 2.
  • an array of pits is provided on a wall surface where the front cover 1 and the rear cover 3 are connected to the blade 4.
  • the pit array includes multiple rows by multiple rows of pits.
  • the number of pits is 10, and each pit includes a plurality of oval pits that are evenly spaced along the flow direction of the blades 4.
  • the 10-row pits make the impeller flow path into 11 flow directions along the blades 4.
  • Each of the shunt channels includes a plurality of oval dimples that are evenly spaced in the circumferential direction with the center line of the impeller as the center.
  • the long axis of each elliptical dimple is arranged along the streamline direction of the blade 4.
  • the length of the major axis of the oval pit is 2mm and the length of the minor axis is 1.5mm.
  • Oval pit depth is h
  • the thickness of the front cover 1 is B 1
  • the thickness of the cover plate 3 is B 2
  • h B 1 + B 2/20.
  • the distribution range of each row of pits in the direction from the blade exit edge 2 to the blade inlet edge is 0.5D 2 to 1.0D 2 , where D 2 is the diameter of the impeller outlet.
  • Elliptical dimples are arranged on the front cover 1 and rear cover 3 along the flow direction of the blades 4, and the parameters of the oval dimples are quantified. Compared with the circular dimples, the oval dimples run along the blades 4.
  • the arrangement in the streamline direction is more suitable for the flow of fluid on the front cover 1 and the rear cover 3, and the disturbance of the turbulent structure of the boundary layer is more intense, so that the drag reduction effect is better.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Geometry (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)

Abstract

一种基于耦合仿生优化的叶片泵叶轮，包括前盖板（1）、后盖板（3）和叶片（4），叶片（4）的工作面和背面上位于叶轮出口处设有多个相互平行的V形槽（5，6），V形槽（5，6）从叶片出口（2）边向叶片进口边的方向延伸，前盖板（1）和后盖板（3）均设有椭圆形凹坑阵列，每列凹坑均沿叶片流线方向均匀设置，每行凹坑均以叶轮的中线为中心沿圆周方向均匀设置。通过在叶片的工作面与背面上开设V形槽组进行仿生优化，并在前盖板（1）和后盖板（3）相对的壁面上设置椭圆形凹坑阵列进行仿生优化，有效降低了叶片表面的阻力，提高泵的减阻效果。

Description

一种基于耦合仿生优化的叶片泵叶轮 技术领域
本发明涉及叶片泵仿生减阻领域，尤其涉及一种基于耦合仿生优化的叶片泵叶轮。
背景技术
鲸鱼、鲨鱼、海豚等位于食物链高端的海洋生物，经过漫长的自然进化和生物选择，迄今为止已具备了卓越的运动能力和生存能力：低能耗长距离巡航、敏锐的感知定位能力、优异的自我保护和巡游波动小等能力，这其中的能力都是目前水力机械以及水下航行体期望达到的目标，因此利用仿生原理进行减阻的理论和应用技术研究已成为目前国内外研究的热点，将仿生非光滑表面独有的经济、环保、减阻和降噪特性应用在了军工、汽车和航空航天等行业中。
经检索，中国专利申请号：CN201410040097.9，名称为：双涡轮液力变矩器导轮仿生叶片，将导轮叶片的外轮廓由叶片前缘、压力面轮廓、吸力面轮廓和叶片尾部平滑连接构成海豚形状。该发明所述的双涡轮液力变矩器导轮仿生叶片克服了现有技术中由于双涡轮液力变矩器导轮叶片前缘肥大、边缘曲线曲率不连续、中间流线不合理等因素等造成液流流经导轮后的能量损失较大的问题，双涡轮液力变矩器导轮仿生叶片，曲线过度光滑平整，结构简单，制造容易，可有效提高双涡轮液力变矩器的性能。
发明内容
针对现有技术中存在不足，本发明提供了一种基于耦合仿生优化的叶片泵叶轮，提高泵的减阻效果。
本发明是通过以下技术手段实现上述技术目的的。
一种基于耦合仿生优化的叶片泵叶轮，包括前盖板、后盖板和叶片，所述叶片的工作面上位于叶轮出口处设有多个相互平行的第一V形槽，所述第一V形槽从叶片出口边向叶片进口边的方向延伸，所述第一V形槽的长度Lg为整个叶片长度的四分之一，所述第一V形槽的导向与所述叶片出口边的夹角θ 1为95°；
所述叶片的背面上位于叶轮出口处设有多个相互平行的第二V形槽，所述第二V形槽从叶片出口边向叶片进口边的方向延伸，所述第二V形槽的长度L b为整个叶片的长度的三分之一，所述第二V形槽的导向与所述叶片出口边的夹角θ 2为85°；
所述前盖板和后盖板上均设有凹坑阵列，每列凹坑包括多个沿叶片流线方向均匀间 隔开设置的凹坑，多列凹坑使得叶轮流道被均分为多个沿着叶片流线方向的分流道，每行凹坑包括多个以叶轮的中线为中心沿圆周方向均匀间隔开设置的凹坑。优选地，所述凹坑为椭圆形凹坑，所述椭圆形凹坑的长轴沿叶片流线方向设置。
优选地，所述前盖板与后盖板上的椭圆形凹坑关于前盖板与后盖板之间的中心面相互对称。
优选地，所述椭圆形凹坑的长轴长度为2mm，短轴长度为1.5mm，沿叶轮径向方向相邻两个椭圆形凹坑的中心距离为Ra，Ra＝0.04D 2，其中D 2为叶轮出口直径。
优选地，所述椭圆形凹坑的深度为h，前盖板的厚度为B 1，后盖板的厚度为B 2，h＝(B 1+B 2)/20。
优选地，每列凹坑沿叶轮的出口边至叶片进口边方向的分布范围为0.5D 2～1.0D 2，其中D 2为叶轮出口直径。
优选地，所述凹坑阵列中的列数为10列。
优选地，所述第一V形槽和第二V形槽的深度均为h，h为叶片厚度δ的六分之一，如果叶片为非等厚度叶片，则叶片厚度δ取厚度的最大值。
优选地，所述第一V形槽和第二V形槽的宽度均为S，S为叶片出口边的宽度b 2的二十分之一。
优选地，多个所述第一V形槽形成第一V形槽组，所述第一V形槽组与前盖板和后盖板之间的距离均为叶片出口边宽度b 2的十分之一，多个所述第二V形槽形成第二V形槽组，所述第二V形槽组与前盖板和后盖板之间的距离均为叶片出口边宽度b 2的十分之一。
本发明的有益效果：
1)本发明通过在叶片的工作面与背面上分别开设第一和第二V形槽组进行仿生优化，并在前盖板和后盖板相对的壁面上设置多列乘多行凹坑进行仿生优化，同时对第一和第二V形槽的长度以及第一和第二V形槽的导向与叶片出口边的夹角进行了量化设计，第一和第二V形槽通过减少湍流的产生来控制边界层、降低边界层最底层水流速度，即降低叶片表面与水的结合力从而降低摩擦剪切应力；凹坑改变了前后盖板边界层的流体结构，抑制和延迟紊流的发生，从而有效降低了盖板表面的阻力；
2)本发明在前后盖板沿流线方向布置有椭圆形凹坑，与圆形凹坑相比椭圆形凹坑顺着流线方向布置更适合前后盖板上流体的流动情况，对边界层湍流结构的扰动更加强烈，从而减阻效果更好。
3)第一V形槽的导向与叶片出口边的角度θ 1、第二V形槽与叶片出口边的角度θ 2以及第一V形槽和第二V形槽的高度S和深度h的量化能够使得流体延沟槽方向流动时，径向涡旋只能与沟槽尖顶发生小面积接触，减小对沟槽内壁的剪切力；对于第一V形槽和第二V形槽的长度的量化考虑了加工过程以及叶片强度，可以在保证叶片强度和易加工情况下获得较好的减阻效果。
附图说明
图1为本发明所述基于耦合仿生优化的叶片泵叶轮的结构示意图。
图2为本发明所述叶片的工作面上的第一V形槽组的结构示意图。
图3为本发明所述叶片的背面上的第二V形槽组的结构示意图。
图4为本发明所述第一V形槽的结构示意图。
图5为本发明所述前盖板或后盖板上凹坑的示意图。
图中：
1.前盖板；2.叶片出口边；3.后盖板；4.叶片；5.第一V形槽；6.第二V形槽。
具体实施方式
下面结合附图以及具体实施例对本发明作进一步的说明，但本发明的保护范围并不限于此。
如图1所示，本发明所述的一种基于耦合仿生优化的叶片泵叶轮，包括前盖板1、后盖板3和叶片4。
如图2所示，叶片4的工作面上位于叶轮出口处设有多个相互平行的第一V形槽5，第一V形槽5从叶片出口边2向叶片进口边的方向延伸，基于数值计算分析叶片4的工作面边界层剪切力分布情况，第一V形槽5的长度Lg为整个叶片4长度的四分之一，第一V形槽5的导向与叶片出口边2的夹角θ 1为95°，相邻两个第一V形槽5之间的距离为0，多个第一V形槽5形成第一V形槽组，第一V形槽组与前盖板1和后盖板3之间的距离均为叶片出口边2的宽度b 2的十分之一。
如图3所示，叶片4的背面上位于叶轮出口处设有多个相互平行的第二V形槽6，第二V形槽6从叶片出口边2向叶片进口边的方向延伸，基于数值计算分析叶片4背面边界层剪切力分布情况，第二V形槽6的长度L b为整个叶片4长度的三分之一，第二V形槽6的导向与叶片出口边2的夹角θ 2为85°，相邻两个第二V形槽6之间的距离为0，多个第二V形槽6形成第二V形槽组，第二V形槽组与前盖板1和后盖板3之间的距离 均为叶片出口边2宽度b 2的十分之一。第一V形槽5和第二V形槽6通过减少湍流的产生来控制边界层、降低边界层最底层水流速度，即降低叶片4表面与水的结合力从而降低摩擦剪切应力。
如图4所示，第一V形槽5和第二V形槽6的深度均为h，h为叶片4的厚度δ的六分之一，如果叶片4为非等厚度，则叶片4的厚度δ取其厚度的最大值。
第一V形槽5和第二V形槽6的宽度均为S，S为叶片出口边2的宽度b 2的二十分之一。
如图1和图5所示，前盖板1和后盖板3与叶片4连接的壁面上均设有凹坑阵列，凹坑阵列包括多列乘多行凹坑，本实施例中，凹坑的列数为10列，每列凹坑包括多个沿叶片4流线方向均匀间隔开设置的椭圆形凹坑，10列凹坑使得叶轮流道被分为11个沿着叶片4的流向的分流道，每行包括多个以叶轮的中线为中心沿圆周方向均匀间隔开设置的椭圆形凹坑。每个椭圆形凹坑的长轴沿叶片4的流线方向设置。椭圆形凹坑的长轴长度为2mm，短轴长度为1.5mm，沿叶轮径向方向相邻两个椭圆形凹坑的中心的距离为Ra，Ra＝0.04D 2，其中D 2为叶轮出口直径。
椭圆形凹坑的深度为h，前盖板1的厚度为B 1，后盖板3的厚度为B 2，h＝B 1+B 2/20。
每列凹坑沿叶片出口边2至叶片进口边方向的分布范围为0.5D 2～1.0D 2，其中D 2为叶轮出口直径。在前盖板1和后盖板3上沿叶片4流线方向布置椭圆形凹坑，并量化了椭圆形凹坑的相关参数，与圆形凹坑相比椭圆形凹坑顺着叶片4的流线方向布置更适合前盖板1和后盖板3上流体的流动情况，对边界层湍流结构的扰动更加强烈，从而减阻效果更好。
所述实施例为本发明的优选的实施方式，但本发明并不限于上述实施方式，在不背离本发明的实质内容的情况下，本领域技术人员能够做出的任何显而易见的改进、替换或变型均属于本发明的保护范围。

Claims (10)

  1. 一种基于耦合仿生优化的叶片泵叶轮，包括前盖板(1)、后盖板(3)和叶片(4)，其特征在于，所述叶片(4)的工作面上位于叶轮出口处设有多个相互平行的第一V形槽(5)，所述第一V形槽(5)从叶片出口边(2)向叶片进口边的方向延伸，所述第一V形槽(5)的长度Lg为整个叶片(4)长度的四分之一，所述第一V形槽(5)的导向与所述叶片出口边(2)的夹角θ 1为95°；
    所述叶片(4)的背面上位于叶轮出口处设有多个相互平行的第二V形槽(6)，所述第二V形槽(6)从叶片出口边(2)向叶片进口边的方向延伸，所述第二V形槽(6)的长度L b为整个叶片(4)长度的三分之一，所述第二V形槽(6)的导向与所述叶片出口边(2)的夹角θ 2为85°；
    所述前盖板(1)和后盖板(3)上均设有凹坑阵列，每列凹坑包括多个沿叶片(4)流线方向均匀设置的凹坑，多列凹坑使得叶轮流道被均分为多个沿着叶片(4)流线方向的分流道，每行凹坑包括多个以叶轮的中线为中心沿圆周方向均匀设置的凹坑。
  2. 根据权利要求1所述的基于耦合仿生优化的叶片泵叶轮，其特征在于，所述凹坑为椭圆形凹坑，所述椭圆形凹坑的长轴沿叶片(4)的流线方向设置。
  3. 根据权利要求2所述的基于耦合仿生优化的叶片泵叶轮，其特征在于，所述前盖板(1)与后盖板(3)上的椭圆形凹坑关于前盖板(1)与后盖板(3)之间的中心面相互对称。
  4. 根据权利要求2所述的基于耦合仿生优化的叶片泵叶轮，其特征在于，所述椭圆形凹坑的长轴长度为2mm，短轴长度为1.5mm，沿叶轮径向方向相邻两个椭圆形凹坑的中心距离为Ra，Ra＝0.04D 2，其中D 2为叶轮出口直径。
  5. 根据权利要求2所述的基于耦合仿生优化的叶片泵叶轮，其特征在于，所述椭圆形凹坑的深度为h，前盖板(1)的厚度为B 1，后盖板(3)的厚度为B 2，h＝(B 1+B 2)/20。
  6. 根据权利要求1所述的基于耦合仿生优化的叶片泵叶轮，其特征在于，每列凹坑沿叶片出口边(2)至叶片进口边方向的分布范围为0.5D 2～1.0D 2，其中D 2为叶轮出口直径。
  7. 根据权利要求1所述的基于耦合仿生优化的叶片泵叶轮，其特征在于，所述凹坑阵列中的列数为10列。
  8. 根据权利要求1所述的基于耦合仿生优化的叶片泵叶轮，其特征在于，所述第一 V形槽(5)和第二V形槽(6)的深度均为h，h为叶片(4)厚度δ的六分之一，如果叶片(4)为非等厚度，则叶片(4)的厚度δ取厚度的最大值。
  9. 根据权利要求1所述的基于耦合仿生优化的叶片泵叶轮，其特征在于，所述第一V形槽(5)和第二V形槽(6)的宽度均为S，S为叶片出口边(2)的宽度b 2的二十分之一。
  10. 根据权利要求1所述的基于耦合仿生优化的叶片泵叶轮，其特征在于，多个所述第一V形槽(5)形成第一V形槽组，所述第一V形槽组与前盖板(1)和后盖板(3)之间的距离均为叶片出口边(2)宽度b 2的十分之一，多个所述第二V形槽(6)形成第二V形槽组，所述第二V形槽组与前盖板(1)和后盖板(3)之间的距离均为叶片出口边(2)宽度b 2的十分之一。
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