CN113719469A - 一种短排距泥泵叶轮叶片设计方法 - Google Patents
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Abstract
本发明涉及疏浚泥泵水力设计技术领域,一种短排距泥泵叶轮叶片设计方法。为用于3500m3/h绞吸挖泥船短排距施工的泥泵叶轮及设计方法,叶片为三维扭曲叶片。本发明的泥泵短排距叶轮叶片被设计成扭曲型叶片,叶片型线在保证泥泵效率的前提下比通用叶轮扬程降低20m,新的泥泵叶轮能够解决3500m3/h绞吸挖泥船在短排距施工采用管线缩口而造成的能耗浪费问题,减少单位疏浚能耗,提高了该系列绞吸挖泥船在短排距工况施工的疏浚经济性。
Description
技术领域
本发明涉及疏浚泥泵水力设计领域,属于疏浚泥泵、流体力学等跨技术领域。
背景技术
泥泵是挖泥船的关键设备,当挖泥船的排泥管线长度(排距)发生变化时,尤其是短排距工况,泥泵流量过大会造成功率过载,目前挖泥船泥泵多为柴油机直接驱动,转速调节受到限制,只能在排口增加缩口来减小流量,但是增加缩口相当于增加了管阻,缩口相当于“消能器”,浪费了能量。如果通过更换叶轮,改变泥泵的外特性,即短排距时采用低扬程叶轮,进而提高泥泵在较短排距下的适应性,能有效降低挖泥船的施工油耗,节约成本,提高疏浚效益。
目前3500m3/h系列绞吸挖泥船在粉砂施工管线1公里-3公里,排出管路内径850mm,只能通过缩口来降低流速,缩口直径甚至仅300mm,大大增加了不必要的能耗,如能通过更换为低扬程专用泥泵叶轮来控制流速,代替采用缩口的流量调节方式,可以降低施工能耗,节约疏浚成本,提高该系列绞吸挖泥船在短排距工况施工的经济性。
发明内容
现有3500m3/h绞吸船舱内泥泵转速调节受限,在短排距工况的泥泵扬程过高、流量过大,为防止泥泵功率过载,不得不采用管线缩口来降低流量,但是缩口造成能耗浪费,为此本发明提供了一种低扬程的泥泵叶轮设计方法,采用该叶轮设计的泥泵扬程比原叶轮降低20m,且效率达到86%,与采用管线缩口的实施效果相比,在短排距工况,单位能耗降低10%以上,有效减少柴油机驱动这类设备的燃油消耗,提高了挖泥船的施工经济性。
本发明需要保护的技术方案是:
一种短排距泥泵叶轮叶片设计方法,其特征在于,叶片型线方程由两部分组成,包括叶片与前盖板交线方程和叶片与后盖板交线方程:
叶片与前盖板交线方程,如下
叶片与后盖板交线方程,如下
其中,r1为叶轮吸口半径,单位mm;θ为叶片在圆周方向的角度,叶片前盖板交线进口为起始20°,叶片后盖板交线进口为起始0°,叶片出口为终点 为叶片包角,rs(θ)和rh(θ)分别为前盖板交线和后盖板交线上任一点到叶轮中心的距离,单位mm。
上述设计方法得到的叶片,为扭曲型叶片(3),采用三个扭曲型叶片(3)可应用于悬臂式闭式离心叶轮的设计,可获得低扬程泥泵叶轮,其特征在于,包括叶轮前盖板(1)、导流帽(2)、叶片(3)、叶轮后盖板(4)、轮毂(5)围成(位置关系,连接关系都已属于现有技术),构成了叶轮的过流部分;所述的叶片3为扭曲型叶片,叶片数为3个,圆周均布,叶片厚度取值为60~90mm,叶片出口宽度B2为叶轮吸口直径D1的42.5%,叶轮流道通过最大球体直径为叶轮吸口直径D1的42%,叶片包角取值140°~165°,且叶片后盖板交线的包角比叶片前盖板交线的包角大20°。
上述设计方法获得的一种泥泵叶轮,应用于绞吸挖泥船短排距施工。
上述泥泵叶轮,应用于绞吸挖泥船短排距施工。实施时,可以设计一种低扬程、低功率的高效泥泵,仅通过更换本发明的悬臂式闭式离心叶轮以降低泥泵扬程,泥泵内腔由本发明悬臂式闭式离心叶轮及单流道泵壳组成,内部的叶轮及外部的泵壳均采用高铬铸铁铸造而成。
泵轴与叶轮轮毂通过螺纹连接,叶轮吸口有防磨环,吸口处有防磨衬套,叶轮与泵盖间有防磨衬板。
泵壳由衬板、泵盖支撑并固定,泵壳流道断面形状为圆角矩形,泵壳流道宽度值取叶轮流道宽度与叶轮前后盖板厚度值以及叶轮盖板与耐磨衬板的间隙值之和,叶轮前后盖板厚度值取50-60mm,叶轮盖板与耐磨衬板的间隙值取3-5mm,泵壳的内、外缘均为螺旋线型。
本发明的泥泵叶轮叶片被设计成扭曲型叶片,叶片型线降低了扬程,提高了泥泵效率,本发明泥泵叶轮能够解决短排距工况下泥泵流量过大而功率过载的问题,减少燃油消耗,避免能耗浪费。
本发明的泥泵具有耐磨、高效率,清水效率可以达到86%;在短排距工况,与管线缩口方案相比,本发明节能10%以上,提高了施工经济型,给企业带来了明显的效益提升。
附图说明
图1为本实施例叶轮轴面投影图和叶片型线图。
图2为三维叶轮零件图,1-前盖板,2-导流帽,3-叶片,4-后盖板,5-轮毂。
图3为叶轮水体流道三维图以及通过球径图。
图4为双壳泥泵三维装配图,6-泵壳,7-耐磨衬板,8-大盖,9-前盖,10-叶轮,11-叶轮吸口防磨环,12-外壳,13-轴承筒组件,14-泵轴,15-轴承座。
具体实施方式
下面结合附图对本发明作进一步说明:
图1所示,叶轮流道轴面投影和叶片型线,叶片(3)数为3,叶轮外径D2为2504mm,叶轮吸口直径D1为900mm,叶轮流道出口宽度B2为叶轮吸口直径D1的42.5%,即叶轮流道出口宽度B2为382.5mm,叶片包角取155°,根据方程(1)和方程(2)计算得到叶片型线坐标如下表。叶片由前盖板交线rs(θ)和后盖板交线rh(θ)放样后,向叶轮外缘方向加厚80mm。
θ | 0 | 10 | 20 | 30 | 40 | 50 | 60 | 70 | 80 | 90 | 100 | 110 | 120 | 130 | 140 | 150 | 155 |
r<sub>s</sub>(θ) | 407 | 439 | 474 | 511 | 552 | 595 | 642 | 693 | 748 | 807 | 871 | 936 | 1006 | 1076 | 1147 | 1217 | 1252 |
r<sub>h</sub>(θ) | 511 | 546 | 582 | 622 | 663 | 708 | 755 | 806 | 860 | 936 | 1006 | 1076 | 1147 | 1217 | 1252 |
图2所示,叶轮的过流部分由叶轮前盖板1、导流帽2、叶片3和叶轮后盖板4、轮毂5围成,且前述五个部分为一体铸造。叶片3为扭曲型叶片,叶片数为三个,叶轮流道通过最大球体直径为叶轮吸口直径的42%。
图3所示,本发明叶轮的最大通过球体直径为图1中叶轮吸口直径D1的42%,即378mm。
图4所示,泵轴14与叶轮10通过螺纹连接,叶轮10与叶轮吸口防磨环11通过螺栓连接,叶轮10位于泵壳6以及耐磨衬板7组成的腔体内,泵壳6通过螺栓固定在外壳12上,泵壳6与外壳12之间的腔体充满高压水已平衡泥泵流道内的压力,叶轮10与前盖9和外壳12间有耐磨衬板7,耐磨衬板7通过螺栓和前盖9和外壳12连接,前盖9通过螺栓连接在大盖8上,大盖8通过螺栓连接在外壳12上,泵轴14位于轴承筒13内部,轴承筒13固定在轴承座15上,且轴承座15通过螺栓与外壳7连接,轴承座15和外壳12通过螺栓固定在船体甲板上。
泵壳流道宽度值取叶轮流道宽度与叶轮前后盖板厚度值以及叶轮盖板与耐磨衬板的间隙值之和,叶轮前、后盖板厚度值取60mm,叶轮前、后盖板与耐磨衬板的间隙值取4mm,即泵壳流道宽度值取510.5mm。
图5所示,经过数值模拟仿真得到本发明泥泵的性能曲线,流量11000m3/h,水力效率可达86%,通用叶轮的扬程80m,本发明的短排距叶轮扬程60m。经测试实践(表1),在某疏浚工程,输送管线直径850mm,排距3km,根据本发明设计的叶轮减少了管线缩口的使用,有效避免了燃油浪费,在短排距工况实验的单位疏浚能耗降低了13.4%,施工180小时左右,节约燃油共计30吨,提高了挖泥船的施工经济性,具有较高的经济效益。
表1更换叶轮前后各180小时生产资料统计对比
土方累计m<sup>3</sup> | 生产率m<sup>3</sup>/h | 总油耗t | 万方油耗t | 缩口直径mm | |
通用叶轮 | 393500 | 2146 | 238.0 | 6.05 | 450 |
本发明的短排距叶轮 | 397130 | 2199 | 208.0 | 5.24 | 无 |
对比% | 0.92 | 2.46 | -12.61 | -13.40 |
本领域对叶轮即泥泵的降耗设计,惯用的方法有切割叶轮、柴油机降低转速等;本领域公知,它们通常能改良达到的效果是疏浚能耗降低3%-5%。本发明最优实施例(为155°)13.4%疏浚能耗降低率,在本领域为罕见。
以上为本发明专利的具体说明,但本发明并不限于上述实施例,也包含本发明构思范围内的其他实施例或变形例。
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