螺旋桨设计计算说明书

某沿海单桨散货船螺旋桨设计计算说明书1.已知船体的主要参数船长L=118.00米型宽B=9.70米设计吃水T=7.20米排水量△=5558.2吨方型系数CB=0.658桨轴中心距基线高度Zp=3.00米由模型试验提供的船体有效马力曲线数据如下：航速V（kn）13141516有效马力PE（hp）21602420300540452.主机参数型号6ESDZ58/100柴油机额定功率Ps=5400hp额定转速N=165rpm转向右旋传递效率ηs=0.983.相关推进因子伴流分数w=0.279推力减额分数t=0.223相对旋转效率ηR=1.0船身效率0777.111wtH4.可以达到最大航速的计算采用MAU四叶桨图谱进行计算。取功率储备10%，轴系效率ηs=0.98螺旋桨敞水收到马力：PD=RsSP9.0=0.9×5400×0.98×1.0=4762.8hp根据MAU4-40、MAU4-55、MAU4-70的Bp--δ图谱列表计算：项目单位数值假定航速Vkn13141516VA=(1-w)Vkn9.37310.09410.81511.536Bp=NPD0.5/VA2.542.33735.17729.60425.193Bp6.5075.9315.4415.019MAU4-40δ76706461P/D0.620.650.690.71ηO0.560.5830.6050.625PTE=PD·ηH·ηOhp2874.412992.463105.393208.04MAU4-55δ74686360P/D0.70.720.740.76ηO0.5410.5680.590.61PTE=PD·ηH·ηOhp2776.882915.473028.393131.05MAU4-70δ74676259P/D0.710.730.760.78ηO0.5210.5460.570.588PTE=PD·ηH·ηOhp2674.232802.552925.743018.13据上表的计算结果可绘制PTE、δ、P/D及ηO对V的曲线，如图1所示。（见所附坐标纸）从PTE—f(V)曲线与船体满载有效马力曲线之交点，可获得不同盘面比所对应的设计航速及螺旋桨最佳要素P/D、D及ηO如下表所列。5.空泡校核按柏利尔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hf=T－Zp=7.2－3.00=4.2mp0－pv=pa+γhs－pv=10300+1025×4.2-174MAUVmaxP/DδDηO4-4015.10.6963.54.190.614-5515.00.74634.130.594-7014.80.75562.54.040.56=14461kgf/m2计算温度t=15°C,Pv=174kgf/m2,PD=4762.8hp,ρ=104.63kgfs2/m4序号项目单位数值MAU4-40MAU4-55MAU4-701VmaxKn15.11514.82VA=0.5144Vmax(1-w)m/s5.65.565.493(0.7πND/60)2(m/s)2641.43623.19596.334V20.7R=V2A+32(m/s)2672.79654.14626.465σ=(p0-pv)/21ρV0.7R20.410.420.446Τc0.1650.1670.1737T=PD·ηO·75/VAkgf38908.1237883.3236442.968AP=T/21ρV0.7R2·τcm26.706.636.439AE=AP/(1.067-0.229P/D)m27.377.397.1910AE/AO=AE/41πD20.5340.5510.561按上述结果作图2(见所附坐标纸),可求得不发生空泡的最小盘面比以及对应的最佳螺旋桨要素AE/AO=0.55P/D=0.74D=4.13mηo=0.59Vmax=15.0kn6.强度校核按1983年规范校核t0.25R及t0.6r,应不小于按下式计算之值:t=XKY,ZbNNAYe1,X=A2GAdN2D3/1010Zb计算功率Ne=5400×0.98=5292hpAD=AE/AO=0.55,P/D=0.74,8，G=7.6gf/cm3,N=165rpmb0.66R=0.226D·AE/AO/0.1Z=0.226×4.13×0.55÷0.4=1.2834mb0.25R=0.7212b0.66R=0.9256b0.6R=0.9911b0.66R=1.2720项目单位数值0.25R0.6R弦长bm0.92561.272K1634207K2250151K31410635K4434A1=D/P(K1-K2D/P0.7)+K3D/P0.7-K42301.62828.09Y=A1Ne/ZbN19938.255219.94K58223K63412K74165K8380330A2=D/P(K5+K6ε)+K7ε+K81186.381010.81材料系数K（铝镍合金）1.1791.179X=A2GAdN2D3/1010Zb0.2570.159)(XKYtmm147.0571.55MAU标准桨叶厚度t′mm15890校核结果满足要求满足要求实取桨叶厚度mm16092实取桨叶厚度按t1.0R=0.0035D=14.46mm与t0.25R=160mm连直线决定:t0.2R=169.7mmt0.3R=150.3mmt0.4R=130.9mmt0.5R=111.5mmt0.6R=92.1mmt0.7R=72.7mmt0.8R=53.3mmt0.9R=33.9mm7.螺距修正根据尾轴直径大小，决定毂径比dh/D=0.18，此值与MAU桨标准毂径比相同，故对此项螺距无需修正。由于实际桨叶厚度大于MAU桨标准厚度，故需因厚度差异进行螺距修正。设计桨)(bt0.7R=0.0727/(0.9964×1.2834)=0.05685标准桨)(bt0.7R=0.0171×4.13/(0.9964×0.31075×4.13)=0.055221－s=NPVA=NPV866.30)­1(=0.721×15×30.866/165/3.0526=0.6628△)(bt0.7R=〔)(bt0.7R设－)(bt0.7R标×51.055.0〕×0.75=-0.0000055△)(DPt=－2)(DP0(1－s)△)(bt0.7R=-2×0.74×0.6628×(-0.0000055)=0.000005395修正后的螺距比：DP=)(DP0＋△)(DPt=0.74+0.000005395=0.748.重量及惯性矩计算每叶片重量=（1/3×1.613952÷10×2.065+0.166×0.02×2.065）×7600=896.39kgf4个叶片重量=4×896.39=3585.56kgf桨毂重量=2835.8kgf整个螺旋桨重量=3585.56+2835.8=6421.36kgf每叶片体积惯性矩=1/3×2.065÷10×1.951+0.166×0.02×2.065×0.19×2.065×0.19×2.065=0.135m5每叶片质量惯性矩=7600/9.8×0.135=104.7kgf·m·s24个叶片质量惯性矩=4×104.7=418.8kgf·m·s2桨毂转动惯性矩=34.3kgf·m·s2整个螺旋桨的惯性矩=418.8+34.3=453.1kgf·m·s2=45310kgf·cm·s29.敞水特性曲线由于校核后所得盘面比AE/AO=0.55，所以无需由MAU4-40,MAU4-55,P/D=0.74的敞水特性曲线内插得到MAU4-55,P/D=0.74的敞水特性曲线，可以直接从课本附录中MAU4-55KT,KQ-J图查得数据，其数据如下：设计桨的敞水特性数据表J00.10.20.30.40.50.60.710KQ0.370.340.320.280.250.210.160.12KT0.320.30.270.240.20.150.110.0510.螺旋桨计算总结螺旋桨直径4.13m螺距比0.74型式MAU叶数Z=4盘面比0.55纵倾角8螺旋桨效率0.59设计航速15.0kn毂径比dh/D=0.18旋向右旋材料铝镍青铜重量6421.36kg惯性矩45310kgf·cm·s2（1）（2）（3）（4）（5）（6）（7）（8）（9）（10）r/R面积系数Ka弦长╳最大厚度b╳t切面面积(m2)S=Kabt辛式系数SM(4)╳(5)rr2(6)╳(7)(6)╳(8)0.20.6740.854×0.16770.09710.0970.4130.1710.0400.0160.30.6740.097×0.14830.09940.3960.6200.3840.2470.1530.40.6741.118×0.12890.09720.1940.8260.6820.1600.1330.50.67451.21×0.10940.08940.3561.0321.0660.3680.3810.60.67451.271×0.090.07720.1541.2391.5350.1910.2370.70.6771.279×0.0710.06140.2441.4462.0890.3550.5140.80.6831.193×0.0510.04220.0841.6522.7290.1370.2270.90.6950.945×0.0320.02140.0821.8593.4540.1560.29010.70×0.01240102.0654.26400∑(6)=1.614∑(9)=1.656∑(10)=1.951