A、y<sub>n+1sub>〉y<sub>nsub>〉y<sub>n-1sub> B、y<sub>n+1sub>〈y<sub>nsub>〈y<sub>n-1sub> C、y<sub>n+1sub>=y<sub>nsub>=y<sub>n-1sub> D、不确定
A、y<sub>n+1sub>〉y<sub>nsub>〉y<sub>n-1sub> B、y<sub>n+1sub>〈y<sub>nsub>〈y<sub>n-1sub> C、y<sub>n+1sub>=y<sub>nsub>=y<sub>n-1sub> D、不确定
A、Y<sub>Fa1sub>≤Y<sub>Fa2sub> B、Y<sub>Fa1sub><Y<sub>Fa2sub> C、Y<sub>Fa1sub>=Y<sub>Fa2sub> D、Y<sub>Fa1sub>>Y<sub>Fa2sub>
A、a=2X<sub>1sub>-X<sub>2sub> B、a=2X<sub>2sub>-X<sub>1sub> C、a=X<sub>1sub>-2X<sub>2sub> D、a=X<sub>2sub>-2X<sub>1sub>
A、x'<sub>1sub>>x<sub>1sub>和y'<sub>1sub>>y<sub>1sub> B、x'<sub>1sub><x<sub>1sub>和y'<sub>1sub><y<sub>1sub> C、x'<sub>1sub>=x<sub>1sub>和y'<sub>1sub>=y<sub>1sub> D、不确定
A、Y<sub>Fa1sub><y<sub>Fa2 B、Y<sub>Fa1sub>>Y<sub>Fa2sub> C、Y<sub>Fa1sub>=Y<sub>Fa2sub> D、条件不足,无法判断 y<sub>
A、A<sub>2sub>=0;Y<sub>2sub>=1 B、A<sub>2sub>=0;Y<sub>2sub>=0 C、A<sub>2sub>=1;Y<sub>2sub>=1 D、A<sub>2sub>=1;Y<sub>2sub>=0
A、Y<sub>t-1sub>,G<sub>tsub> B、I<sub>tsub>,Y<sub>tsub>,C<sub>tsub> C、Y<sub>t-1sub> D、I<sub>tsub>,Y<sub>t-1sub>
A、A3=A4=1,Y<sub>3sub>=1 B、A3=A4=1,Y<sub>3sub>=0 C、A3=A4=0,Y<sub>3sub>=0 D、A3=A4=0,Y<sub>3sub>=1
A、A5=A6=1,Y<sub>4sub>=1 B、A5=A6=1,Y<sub>4sub>=0 C、A5=A6=0,Y<sub>4sub>=0 D、A5=A6=0,Y<sub>4sub>=1
A、以下所示的结构设计简图中,已知轴的转速n=1470r/min,角接触轴承1上的径向载荷R<sub>1sub>=800N,角接触轴承2上的径向载荷R<sub>2sub>=1900N,轴向载荷F<sub>asub>=1200N,两个轴承的额定动载荷C<sub>rsub>均为C<sub>rsub>=38600N,e=0.68,S=0.7R,A/R≤e,x=1,y=0;A/R>e,x=0.41,y=0.87,f<sub>tsub>=1.1,f<sub>psub>=1.2,求受载最大的轴承的工作寿命L<sub>hsub>。