Abstract
In order to realize the low noise design of marine gearbox, a layout method of damping materials for gearbox based on acoustic contribution was proposed. The present method can accurately and effectively determine the additional area of damping materials and achieve greatly the noise reduction effect. Firstly, taking a marine single-stage herringbone gearbox as the object, the finite element/boundary element model for the reducer structure was established. After applying the vibration excitation of the gear system, the radiated noise of each field point was solved. Secondly, by analyzing the acoustic transfer vector (ATV) and modal acoustic contribution (MAC), the surface of the gearbox was partitioned, and the partitioned surface was analyzed by using panel acoustic contribution (PAC). Finally, the damping material was added to the plate area which contributes greatly to the radiated noise, and the effect of the noise reduction under different schemes were compared. The results show that the layout design of damping materials based on the present method can reduce the radiation noise of observation points accurately and effectively in the range of 0~4 000 Hz.
Highlights
目前结构表面阻尼材料的布局设计主要基于结 构拓扑优化方法和模态分析方法[3] 。 Marcelin[4] 等 基于遗传算法对梁结构的附加阻尼材料布局进行优 化设计,但仅限于对阻尼敷设位置的探讨,并未明确 给出最终的阻尼布局。 Sainsbury 等[5] 采用有限单 元法探讨了圆柱壳结构局部覆盖约束阻尼材料的最 小面积布局问题。 Kumar 等[6] 依据薄板指定模态下
Optimization Design of Damping Disk Based on Finite Element Analysis[ J]
In order to realize the low noise design of marine gearbox, a layout method of damping materials for gear⁃ box based on acoustic contribution was proposed
Summary
目前结构表面阻尼材料的布局设计主要基于结 构拓扑优化方法和模态分析方法[3] 。 Marcelin[4] 等 基于遗传算法对梁结构的附加阻尼材料布局进行优 化设计,但仅限于对阻尼敷设位置的探讨,并未明确 给出最终的阻尼布局。 Sainsbury 等[5] 采用有限单 元法探讨了圆柱壳结构局部覆盖约束阻尼材料的最 小面积布局问题。 Kumar 等[6] 依据薄板指定模态下 寸为:长 1 250 mm,宽 600 mm,高 900 mm,如图 4 所示。 由于有限元 / 边界元法在中低频段的辐射噪声 更为准确[19] ,结合单元尺寸和声场参数,最终确定 4 000 Hz 为计算频率上限。 最终使用有限元 / 边界 元方法对各场点的辐射噪声进行了计算,求解得到 的场点 1 和场点 2 的辐射噪声频谱如图 7 所示。 可 以看到在 0 ~ 4 000 Hz 范围内辐射噪声的峰值频率 均为 766.67 Hz 的倍数,原因是减速箱对应齿轮副 的齿数为 23,在 2 000 r / min 工况下的啮合频率为 766.67 Hz。 场点 1、2 在啮合频率及倍频处的声压 级峰值如表 2 所示。
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