振动与冲击
振動與遲擊
진동여충격
JOURNAL OF VIBRATION AND SHOCK
2015年
10期
12-19
,共8页
邓四二%孙朝阳%顾金芳%崔永存
鄧四二%孫朝暘%顧金芳%崔永存
산사이%손조양%고금방%최영존
深沟球轴承%低噪音%表面波纹度%振动
深溝毬軸承%低譟音%錶麵波紋度%振動
심구구축승%저조음%표면파문도%진동
deep groove ball bearing%low-noise%surface waviness%vibration
在滚动轴承动力学分析理论基础上建立含轴承零件工作表面波纹度的深沟球轴承动力学数学模型,并以某型号低噪音深沟球轴承为例,对不同结构参数、工况参数及谐波参数下低噪音深沟球轴承的振动特性进行理论分析。结果表明,合理选取径向游隙、内外沟曲率半径系数及保持架兜孔间隙等参数能使轴承本身达到减振降噪目的;振动值随轴承宽度增加逐渐减小;施加一定轴向载荷能有效降低轴承振动;存在的合理转速使用范围能有效降低轴承振动;内外滚道谐波阶次等于钢球数目整数倍时,轴承振动明显加剧;外滚道激励谐波对应的激励频率为 kzfc ,内滚道激励谐波对应的激励频率为 kzfc +fs;偶次谐波阶次钢球表面波纹度对轴承振动有激励作用;轴承旋转套圈会激励更大的轴承振动值;瞬时载荷增加或瞬时速度提高均会致轴承振动增大。
在滾動軸承動力學分析理論基礎上建立含軸承零件工作錶麵波紋度的深溝毬軸承動力學數學模型,併以某型號低譟音深溝毬軸承為例,對不同結構參數、工況參數及諧波參數下低譟音深溝毬軸承的振動特性進行理論分析。結果錶明,閤理選取徑嚮遊隙、內外溝麯率半徑繫數及保持架兜孔間隙等參數能使軸承本身達到減振降譟目的;振動值隨軸承寬度增加逐漸減小;施加一定軸嚮載荷能有效降低軸承振動;存在的閤理轉速使用範圍能有效降低軸承振動;內外滾道諧波階次等于鋼毬數目整數倍時,軸承振動明顯加劇;外滾道激勵諧波對應的激勵頻率為 kzfc ,內滾道激勵諧波對應的激勵頻率為 kzfc +fs;偶次諧波階次鋼毬錶麵波紋度對軸承振動有激勵作用;軸承鏇轉套圈會激勵更大的軸承振動值;瞬時載荷增加或瞬時速度提高均會緻軸承振動增大。
재곤동축승동역학분석이론기출상건립함축승령건공작표면파문도적심구구축승동역학수학모형,병이모형호저조음심구구축승위례,대불동결구삼수、공황삼수급해파삼수하저조음심구구축승적진동특성진행이론분석。결과표명,합리선취경향유극、내외구곡솔반경계수급보지가두공간극등삼수능사축승본신체도감진강조목적;진동치수축승관도증가축점감소;시가일정축향재하능유효강저축승진동;존재적합리전속사용범위능유효강저축승진동;내외곤도해파계차등우강구수목정수배시,축승진동명현가극;외곤도격려해파대응적격려빈솔위 kzfc ,내곤도격려해파대응적격려빈솔위 kzfc +fs;우차해파계차강구표면파문도대축승진동유격려작용;축승선전투권회격려경대적축승진동치;순시재하증가혹순시속도제고균회치축승진동증대。
Based on the dynamic analysis theory of rolling bearings,a dynamic model for deep groove ball bearings considering the effects of bearing components'working surface waviness was established.Taking a type of low-noise deep groove ball bearing as an example,the bearing vibration characteristics were analyzed theoretically with various bearing structural parameters,working conditions and working surface wavinesses.The results showed that the bearing basic vibration can be reduced by selecting reasonable primary parameters,for instance,bearing radial clearance,inner and outer raceway groove curvature radius coefficients,pocket clearance of cage,and so on;the larger the bearing width,the smaller the bearing vibration;a certain axial loads can reduce effectively the bearing vibration;there is a reasonable rotating speed range for smaller bearing vibration;the severe vibration occurs when the inner and outer raceway surface waviness orders are an integer multiple of the number of balls;the exciting frequency corresponding the waviness orders of outer raceway is kzfc and that of the inner raceway is kzfc +fs;the even waviness orders of ball working surface has an exciting effect on the bearing vibration;the vibration produced by rotating ring is more severe than that of fixed ring;the bearing vibration increases greatly with increase in radial loads or rotating speed.