某沿海单桨散货船螺旋桨设计计算说明书刘磊磊20081013202011年7月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型宽设计吃水排水量方型系数 桨轴中心距基线高度L = 118.00 米B = 9.70 米T = 7.20 米△ = 5558.2 吨CB = 0.658Zp = 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.主机参数额定功率 额定转速 转向传递效率6ESDZ58/100 柴油机Ps = 5400 hpN = 165 rpm右旋n s=0.983.相关推进因子伴流分数 推力减额分数 相对旋转效率船身效率w = 0.279t 二 0.223n r = loi 一 t耳 H 二——二 1.0777H 1 - w4•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n S = 0.98 螺旋桨敞水收到马力：PD = 4762.8 hp根据 MAU4-40、MAU4-55、MAU4-70 的 jBp —6 图谱列表计算:项 目单位数 值假定航速Vkn13141516V=(l—w)VAkn9.37310.09410.81511.536Bp=NP 0.5/V 2.5D A69.01304269.0130469.0130422569.01304225v'BP268.96548323.7116384.6505072451.9996707MAU4-40675.672.1087864.8797736960.744P/D0.640.6673210.6854205610.720498n o0.55833330.5827810.6057068060.62606PTE =PD • n hT Ohp2863.99072989.3953106.9946263211.4377MAU4-55674.62912168.6357663.5658914759.341025P/D0.68600640.7130990.7409584660.7702236n o0.54142170.5671380.5909414380.6111996PTE =PD • n hT Ohp2777.24192909.1563031.2551443135.1705MAU4-70673.77256367.7718563.0305555658.68503P/D0.692540.7231620.7542806390.7861101n o0.52107250.545710.5657927790.5828644Pte=Pd n hT ohp2672.86012799.2382902.25422989.8239据上表的计算结果可绘制PTE、6、P/D及n。
对V的曲线，如下图所示r. C45CC4CCC3oCCPte3CCC2oCC2CCCr. CPytPte1 1li113K1516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n o如下表所列MAUVmaxP/D6Dn O4-4015.1370.6891964.10064.2398766910.6086224-5515.0370.7420163.39984.1658191120.591738724-7014.8510.74960663.686884.1329199360.5630774265•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=4.2mp 0—p v = pa + Y hs — pv = 10300+1025X4.2-174=14461kgf/m2计算温度 t = 15° C ,Pv = 174kgf/ m2 , P° = 4762.8hp, p = 104.63kgfs2/m4序号项目单位数值MAU4-40MAU4-55MAU4-701VmaxKn5.6140468895.5769586495.5079745222VA=0.5144Vmax(1-w)m/s657.4605465634.6935143624.70823133(0.7n ND/60)(m/s)2688.978069665.795982655.04601464V20.7R=V2a+32(m/s)20.4012053340.4151747440.42198818151° =(p0-pv) / 2 P V0.7R20.4012053340.4151747440.4219881816T c（柏利尔空泡限界 图）0.160.1620.1633333337T=Pd ・ n ・ 75/VaOkgf38725.3382337901.4802736517.396181Ap=T /2 p V0.7R2 ・t cm26.7149627736.7169754016.5241950849AE=Ap/(1.067-0.229P/D)m2101Ae/Ao=Ae/4n D27.3857718857.4876015217.286833423按上述结果作图，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 = 0.549200516 P/D二 0.741852486 D= 4.166m n 0=0.591857369 Vmax= 15.03775 knV(kn)15. 215. 0蹲盘0. 580. 550. 52n0. 600. 580. 56P/D0. 760. 720. 68D(m)4. 34. 24. 10.40. 706.强度校核 按1983年＜〈规范＞＞校核10.25R及t0.6r，应不小于按下式计算之值:t= J, Y =樂， X=A GA N2D3/10ioZbK - X ZbN 2 d计算功率 Ne=5400X0.98=5292hpAD = Ae / AO = 0.549200516, P/D=0.741852486, £ = 8。
G=7.6gf/cm3 ,N=165rpmb0.66R =0.226D • Ae / AO/0.1Z=0.226*0.549200516*4.166m/0.4=1.292702683 mb0.25R=0.7212b0.66R = 0.93229717 mb0.6R =0.9911b0.66R = 1.281197629 m项 目单位数 值0.25R0.6R弦长bm634207K1250151K21410635K3434K42297.004326826.6232412A =D/P(K -K D/P )+KD/P -K1 1 2 0.7 3 0.7 419755.287085173.296683Y=AN/ZbN1 e8223K53412K64165K7380330K81185.1838161010.409249A =D/P(K +K £ )+K £ +K2 5 6 7 81.1791.179材料系数K （铝镍合金）0.261120860.161991195X=A GA N2D3/10n)Zb2 d146.706353571.32164252t 二 JY/(K - X)mm159.349590.8188MAU标准桨叶厚度tzmm满足要求满足要求校核结果146.706353585.04785519实取桨叶厚度mm634207t 二0.2R155.5147104mmtt 二0.4R120.2812828mmt 二0.6R85.04785519mmt0.8R = 49.8144276 mmo.3r= 137.8979966 mmto.5R = 102.664569 mmto.7R = 67.43114139 mmto.9R = 32.1977138 mm7.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。
X0.75=-0.002216992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标准桨/t、() =0.055226975b 0.7R1 —s 二VA (1-0 )V X 30.866A = =0.656262685NP NPo.7R=°.°523513813582.9355 kgf6589.59094 kgf10172.53 kgf435.6 kg.m.s"2360.85 kg.m.s"2796.45 kg.m.s"2P p t△ (一)t= —2(—)0(1_s) △ (—) =0.002158685D t ' D 0 ' b 0.7R修正后的螺距比：p p pD=(D )「+△(D )t=°.744011171&重量及惯性矩计算 根据MAU桨切面的面积数据用积分方法计算得: 桨叶重量桨毂重量螺旋桨重量桨叶惯性矩桨毂惯性矩螺旋桨总惯性矩（1）（2）（3）(4)(5)(6)(7)(8)(9)(10)r/R面积系 数Ka弦长X最大 厚度bXt切面面 积(m2) S=Kabt辛式 系数SM（4々（5）rr2(6)x(7)(6)x(8)0.20.6740.1454878570.098058810.0980590.41660.1735560.0408510.0170190.30.674。