螺旋桨课程设计

1、JS813尾滑道渔船螺旋桨设计书指导老师：学生姓名：学号:完成日期:第10页共16页1.船型单桨流线型舵，前倾首柱，巡洋舰尾，柴油机驱动，尾机型尾滑道渔船设计水线长：Lwi_=29.80m垂线间长：LBP=28.00m型宽：B=6.30m型深：D=2.90m设计吃水：T d=2.20m方型系数：Cb=0.555排水量： =222t棱型系数：Cp=0.653纵向浮心坐标Xb= -1.36m纵向浮心位置Xc=%L/ 1/34.92。6431.74宽度吃水比B/T2.86艾亚法有效功率估算表:速度V/Kn91011Froude 数0.270.300.33标准Co （图7-3）332.58270.58

2、223.22标准Cbc0.6250.5770.555实际Cb （肥瘦%）（本船Cb=0.555 ）12.0% （瘦）3.8% （瘦）0Cb修正%8.70%1.88%0Cb修正数量厶128.935.090已修正Cb之C1361.51223.22275.67B/T修正%-4.773-4.773-4.773B/T修正量 217.2510.6513.16已修正B/T之C2378.76233.87288.83标准Xc （L % ）船中后1.30% （后）2.39% （后）2.04% （后）实际Xc （L % ）船中后（本船为后）4.56%4.56%4.56%相差%L，在标准后（本船均为在标准后）3.26

3、%2.52%2.17%Xc修正（% ）4.4%3.2%5.4%Xc修正数量厶3-12.71-9.24-15.60已修正Xc之C3366.05279.60218.27长度修正 %= ( Lwl-1.025Lpp )/Lwl*100%3.7%3.7%3.7%长度修正厶413.5410.348.08已修正长度之C4379.59289.44226.35VA372910001331PE=( a°.64)*(VA3)*0.735/C4(KW)44.8180.47137.20PE=( A°.64)*(VA3)*0.735/C4(hp)60.97109.48186.672 .主机参数型号：

4、8E150C标疋功率：PS2 = 199kw标定转速：750 r/mi n标定马力270.75hp减速后转速：297.62r/mi n减速比：i = 2.52减速箱效率n g：0.96轴系效率n s：0.98最大持续功率：262.63hp相应转速：235.85rpm3推进因子的确定(1) 伴流分数3本船为单桨海上渔船，故使用汉克歇尔公式估算3 =0.77*Cp-0.28=0.222(2) 推力减额分数t，用汉克歇尔公式估算t=0.77*C p-0.3=0.203(3) 相对旋转效率近似地取为n R =1.0(4) 船身效率n h =(1-t)/(1- 3 )=(1-0.203”(1-0.222

5、)=1.0244 .桨叶数Z的选取根据一般情况，单桨船多用四叶，加之四叶图谱资料较为详尽、方便查找,故选用四叶5. AE/AO的估算按公式 Ae/Ao = (1.3+0.3XZ) XT / (po-pv)D2 + k 进行估算， 其中：T=PE/(1-t)V=137.2/(1-0.203 X 11X 0.5144)=30.3kN水温 15C 时汽化压力 pv=174 kgf/m2=174 X 9.8 N/m2=1.705 kN/m2 静压力 p°=pa+ y hs=(10330+1025X 1.5) X 9.8 N/m 2=116.302 kN/m2 k 取 0.2D 允许=0.7X

6、T=0.7 X 2.2=1.5Ae/A0 = (1.3+0.3XZ) XT / (p0-pv)D2 + k=(1.3+0.3X 4)X 30.3/(121.324-1.705)X 2.2X 2.2)+0.2 = 0.4946. 桨型的选取说明由于本船为海上渔船，MAU型原型螺旋桨比较适合在海洋中工作的要 求。所以选用MAU型较适宜。7. 根据估算的AE/A0选取23张图谱根据 AE/A0=0.494选取 MAU4-40, MAU4-55 , MAU4-70 三张图谱。8. 列表按所选图谱（考虑功率储备）进行终结设计，得到3组螺旋桨的要素及VsMAX功率储备取16%，轴系效率n S=0.98,齿

7、轮箱效率n g=0.96螺旋桨敞水收到功率PDO = PsX 0.9X 0.98Xn sXq g=199X 0.84 X 0.98X 0.98 X 0.96 =159.13kw = 213.3 hp (En glish)由图谱可查得：项目单位数量假定航速VKn91011VA=Vs(1-3 )Kn7.007.788.56Bp=n*(PDoP.5)/(VAA2.5)33.5325.7420.28(Bp95)5.795.074.50MAU4-4068.561.255.0P/D0.6750.7160.760n o0.5880.6240.653PTEhp128.43136.29142.63MAU4-55

8、S67.160.054.1P/D0.720.7680.816n o0.5730.6080.636PTEhp125.15132.80138.91MAU4-70S66.559.253.2P/D0.7360.7830.836n o0.5520.5800.607PTEhp120.57126.68132.58相应曲线（如下图1-1所示）得到数据系列/项目Vmax/k nP/DD/mPn oMAU4-4010.350.7331.591.1658.660.636MAU4-5510.290.7821.561.2258.140.617MAU4-7010.220.7941.541.2357.820.586图1-1

9、9 空泡校核，由图解法求出不产生空泡的(Ae/Ao) min及相应的VsMAX、P/D、n 0、D.按柏努利空泡限界线中商船上限线，计算不发生空泡之最小展开面积比。桨轴沉深hs由船体比例取1.5mpo-p v = pa+ y hs-p v =(10330+1025 x 2-174) kgf/m 2 =11591kgf/m2计算温度 t =15°C , p v = 174 kgf/m 2Pdo = 156.78 kw = 213.3 hp (En glish)p =104.63 kgfx W/m4序号项目单位数值MAU4-40MAU4-55MAU4-701AE/Ao0.400.550.

10、702VmaxKn10.3510.2910.223vam/s4.1414.1154.0904(0.7 n ND/60)A2(m/sF2300.82289.58282.205(V(0.7R)A2(m/sF2317.96306.51298.930.5 p (V(0.7R)A216634.0816035.0715638.496cr=(Po-Pv)/(0.5 p(V(0.7R)A2)0.6970.7230.7417T C0.1720.1780.1828T=75*Po* n o/VAKgf2934.12864.42737.29Ap=T/( T C*0.5 pmA21.0261.0040.962(V(0.

11、7R)A2)10AD=Ap/(1.067-0.229*P/D)mA21.1411.1311.08611Ao=n (DA2)/4mA21.9861.9111.86312需要的AE/Ao0.5740.5920.583空泡校核图如下数据分析据上述结果作图二，可求得不发生空泡的最小盘面比及对应的最佳螺旋桨要素：Ae/Ao=O.5923, P/D=0.7884，D=1.5534m，n 0=0.6093，VMAx=lO.l4kn图1-2空泡校核10计算与绘制螺旋桨无因次敞水性征曲线由B4-40,B4-55,P/D=0.735的敞水性征曲线内插得到 B4-50.5, P/D=0.735的敞水性征曲线，其数据

12、如下：J00.10.20.30.40.50.60.70.80.9KT0.34840.31840.27280.250.21280.170.12710.080.03718010KQ0.41840.388460.355640.318460.282820.250.20.15430.08710.0243n 000.122820.250.367180.454360.551540.63590.643080.55898018图1-3螺旋桨无因次敞水性征曲线11.计算船舶系泊状态螺旋桨有效推力与保持转矩不变的转速No由敞水性征曲线得 J=0时，Kt=0.348, Kq=0.0419计算功率 PD=199*0.9

13、6*0.98/0.735=154.72hp 系柱推力减额分数取t0=0.04,主机转矩Q=Pd X 60X 75/(2 冗 N)=254.72X 60X 75/(2 X 3.1416X 297.62)= 612.72 kgf.m系柱推力T=(K t/K q) X (Q/D)=(0.348/0.0419) X (612.72/1.5534)= 3276.01 kgf车叶转速N0=60XVT/( pX D4X Kt)=60 X (3276.01/(104.63X 1.55344X 0.348)0.5=235.85 rpm12 桨叶强度校核按我国1990钢质海船入级与建造规范校核tO.25R及tO.

14、6R，应不小于按下式计算所的之值：t= V Y/(K-X) (mm)式中 Y=A 1X Ne/(Z X bX N),X=A 2X G X Ad X N2X D3/(1010X ZX b)计算功率Ne=262.62hp3Ad= Ae/Ao=O.5923,P/D=0.7884, & =10o, G=7.6gf/cm , N=297.62rpm在0.6R处切面弦长bo.6=2.1867X Ae/Aox D/Z=0.502mbo.25R=O.7212X bo.6R=O.362m项目单位数值0.25R0.60R弦长bm0.3620.502K1634307K2250151K31410635K443

15、4A12186791Y1332.4814347.6605K58223K63412K74165K8380330A213251161材料系数K （铝青 铜）Kgf/cmA31.2001.200X0.13680.08644tmm35.40217.669标准桨叶厚度tAmm59.1833.86校核结果满足要求满足要求实取桨叶厚度mm59.1833.8613桨叶轮廓及各半径切面的型值计算最大切面在0.66R处，bo.66R=O.226*D* A E/Ao/(O.1*Z)=O.52Om轴线处最大厚度 =0.050D=0.050X 1.55X 1000=77.67mm实际桨叶厚度MAU型4叶螺旋桨尺度表列表

16、计算如下：(单位：mm)14 桨毂设计最大连续功率PD=262.63hp，此时No=235.85 rpm(Pd/N)1/3= (582/314.8) 1/3= 1.036根据中文课本P198图9-1可查得螺旋桨桨轴直径dt=150mm采用整体式螺旋桨，则螺旋桨的毂径 dh=1.8dt=1.8X150=270mm毂前后两端的直径 d2=0.88 x dh=0.88 x 270=237.6mmd1=1.10X dh=1.10 x 270=297mm桨毂长度 l0=dh+100=370mm减轻孔的长度 l1=0.3x l0=0.3x 370=111mm毂部筒圆厚度 S =0.75x t0.2R=0.

17、75x 63.07=47.30mm叶面、叶背与毂连接处的圆弧半径r1=0.033D=0.033 x 1553.4 x 1000=53.8mm , r2=0.044D=0.044 x 1.5534 x1000=68.35mm15螺旋桨总图绘制（详见螺旋桨设计总图）附纸rojitKintIr1 ThB.厶1«_k_16. 螺旋桨重量及转动惯量计算铝青铜材料重量密度丫 =8410kgf/m3 , 0.66R处叶切面的弦长bo.6=O.52Omm，螺旋桨直径 D=1.55m t o.2=O.O 6307 m, to.6= 0.03386m最大连续功率 PD=262.63hp，此时N0=235

18、.85 rpm毂径 d=0.167X dt=0.167X 1.5534=00.2700m, 毂长 LK=0.3700m桨毂长度中央处轴径d0 =0.045+0.108(Pd/N)1/3-KL k/2=0.045+0.108X (582/314.8)/3-0.1 X 0.3934/2=0.0666m d/D=0.174则根据我国船舶及海洋工程设计研究院提出的公式： 桨叶重Gbi=0.169 丫 Zbmax(0.5t0.2+t0.6)(1-d/D)D(kgf)=0.169X 8410X 4X 0.520X (0.5X 0.06307+0.03286)X (1-0.174)X 1.5534 =248.06kgf桨毂重Gn=(0.88-0.6d0/d)Lk 丫 d2(kgf)=(0.88-0.6X 0.0666/0.2700)x 0.3700X 8410X 0.27X 0.27 =166.05kgf螺旋桨重量G= Gbl +Gn= 414.1kgf螺旋桨惯性矩I mp=0.0948 丫 Zbmax(0.5t0.2+t0.6)D3=0.0948X 8410X 4X 0.52X (0.5X 0.06307+0.03386)X (1.5534a3)2=406.5kg