6ES7312-1AE13-0AB0

6ES7312-1AE13-0AB0材料彈性力學使得齒輪組嚙合時,主、被動齒輪可簡化為圍繞軸心線旋轉的懸臂梁模型[1]，在承受負荷時會產生彎曲變形, 而且齒面接觸區域存在彈性形變。另外，齒輪制造加工誤差、殼體加工誤差、裝配等各種誤差的客觀影響, 造成齒輪實際嚙合點與理論嚙合區域存在偏移, 產生了嚙合沖擊激勵。為了減少齒輪嚙合時產生的誤差,在設計早期應該對齒輪的NVH做仿真預測。齒形修形是優化齒輪接觸位置和應力大小的有效方法，微觀修形可以針對嚙合的一對齒輪，也可只做單齒輪修形優化，在工程實踐中通常更多采取對單一齒輪修形，其具備較高的生產效率和較低的生產成本。通常齒廓修形的關鍵影響因子有輪廓修形、寬度、齒根和齒頂修形，其中齒根修形參數的確定,需要兼顧修形參數的選擇同時考慮齒軸的系數，避免齒根修形過大引起齒輪齒根彎曲強度的降低。圖4展示了齒廓修形的常規形式，包括左右端直線修形、螺旋線修形和鼓性修形。具體齒廓修形的方案選擇，需綜合考慮輸入負荷激勵的大小、傳遞路徑的剛度及易加工等因素，結合NVH仿真工具優選齒廓修形方案。

綜合修形后各工況負荷下都較好地實現了全齒面接觸，有效避免了邊緣和齒頂受到負荷造成的應力集中，齒面負荷的分布較合理，表明該修形參數下的齒輪接觸斑點位置及大小是可以接受的。

齒輪傳動誤差仿真分析  

輸入級、輸出級齒輪修形后的傳動誤差仿真結果如圖8、圖9所示。

通過對輸入級齒輪修形的傳動誤差分析可以看到：

(1) 在正驅和滑行工況下峰-峰TE都很小。高的峰-峰TE發生在50%驅動模式和50%滑行模式，分別為0.71 μm和0.66 μm，結果優于EV減速器要求的目標值。

(2) 峰-峰TE可以分解到成分諧波(圖8顯示的前三階諧波)中。在所有工況下，TE的主要貢獻是一階諧波并隨著諧波數目的增加而呈指數衰減。

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