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一、填空题1、质量为0.10kg 的物体，以振幅1cm 作简谐运动，其角频率为110s -，则物体的总能量为， 周期为 。
2、一平面简谐波的波动方程为y 0.01cos(20t 0.5x)ππ=-( SI 制)，则它的振幅为 、角频率为 、周期为 、波速为 、波长为 。
3、一弹簧振子系统具有1.0J 的振动能量，0.10m 的振幅和1.0m/s 的最大速率，则弹簧的倔强系数为 ，振子的振动角频率为 。
4、一横波的波动方程是y = 0.02cos2π(100t – 0.4x)( SI 制)则振幅是_________，波长是_ ，频率是 ，波的传播速度是 。
5、两个谐振动合成为一个简谐振动的条件是 。
6、产生共振的条件是振动系统固有频率与驱动力频率 （填相同或不相同）。
7、干涉相长的条件是两列波的相位差为π的 （填奇数或偶数）倍。
8、弹簧振子系统周期为T 。
现将弹簧截去一半，仍挂上原来的物体，作成一个新的弹簧振子，则其振动周期为 。
9、作谐振动的小球,速度的最大值为 ,振幅为 ,则振动的周期为 ;加速度的最大值为 。
10、广播电台的发射频率为 。
则这种电磁波的波长为 。
11、已知平面简谐波的波动方程式为 ,则 时，在X=0处相位为 ，在 处相位为 。
12、若弹簧振子作简谐振动的曲线如下图所示,则振幅 ;圆频率初相 。
13、一简谐振动的运动方程为2x 0.03cos(10t )3ππ=+( SI 制)，则频率ν为 、周期T 为 、振幅A 为 ，初相位ϕ为 。
14、一质点同时参与了两个同方向的简谐振动，它们的振动方程分别为10.05cos(4)()x t SI ωπ=+和20.05cos(1912)()x t SI ωπ=+，其合成运动的方程x ＝ .15、A 、B 是在同一介质中的两相干波源，它们的位相差为π，振动频率都为100Hz ，产生的波以10.0m/s 的速度传播。
波源A 的振动初位相为3π，介质中的P 点与A 、B 等距离，如图所示。
中南大学考试试卷2005 - 2006学年上学期时间门o分钟《机械振动基础》课程32学时1.5学分考试形式：闭卷专业年级：机械03级总分100分，占总评成绩70 %注：此页不作答题纸，请将答案写在答题纸上一、填空题（本题15分，每空1分）1＞不同情况进行分类，振动（系统）大致可分成，（）和非线性振动；确定振动和（）；（）和强迫振动；周期振动和（）；（）和离散系统。
2、在离散系统屮，弹性元件储存（）,惯性元件储存（），（）元件耗散能量。
3、周期运动的最简单形式是（），它是时间的单一（）或（）函数。
4、叠加原理是分析（）的振动性质的基础。
5、系统的固有频率是系统（）的频率，它只与系统的（）和（）有关，与系统受到的激励无关。
二、简答题（本题40分，每小题10分）1、简述机械振动的定义和系统发生振动的原因。
（10分）2、简述振动系统的实际阻尼、临界阻尼、阻尼比的联系与区别。
（10分）3、共振具体指的是振动系统在什么状态下振动？简述其能量集聚过程？（20分）4、多自由系统振动的振型指的是什么？（10分）三、计算题（本题30分）图1 2、图2所示为3自由度无阻尼振动系统。
（1）列写系统自由振动微分方程式（含质量矩阵、刚度矩阵）（10分）；（2）设k t[=k t2=k t3=k t4=k9 /, =/2/5 = /3 = 7,求系统固有频率（10 分）。
13 Kt3四、证明题（本题15分）对振动系统的任一位移{兀},证明Rayleigh商R（x）=⑷严⑷满足材 < 尺⑴ < 忒。
{x}\M\{x}这里，［K］和［M］分别是系统的刚度矩阵和质量矩阵，®和①，分别是系统的最低和最高固有频率。
（提示：用展开定理{x} = y{M} + y2{u2}+……+ y n{u n}）3 •简述无阻尼单自由度系统共振的能量集聚过程。
（10 分） 4.简述线性多自由度系统动力响应分析方法。
（10 分）中南大学考试试卷2006 - 2007学年 上 学期 时间120分钟机械振动 课程 32 学时 2 学分 考试形式：闭卷专业年级： 机械04级 总分100分，占总评成绩 70%注：此页不作答题纸，请将答案写在答题纸上一、填空（15分，每空1分）1. 叠加原理在（A ）中成立；在一定的条件下，可以用线性关系近似（B ） o2. 在振动系统中，弹性元件储存（C ）,惯性元件储存（D ） , （E ）元件耗散 能量。
机械振动考题第一章1.21.If energy is lost in any way during vibration, the system can be considered to be damped. (T)2.Superposition principle is valid for both linear and nonlinear systems(F)3.The frequency with which an initially disturbed system vibrates on its own is known as natural frequency(T)4.Any periodic function can be expanded into Fourier series(T)5.Harmonic motion is a periodic motion(T)6.The equivalent mass of several masses at different locations can be found using the equivalence of kinetic energy(T)7.The generalized coordinates are not necessarily Cartesian coordinates. (T)8.Discrete systems are same as lumped parameter systems(T)9.Consider the sum of harmonic motions,, withand The amplitude A is given by 30.8088(T)10.Consider the sum of harmonic motions, , withand The phase angle α is given by 1.57 rad. (F)第二章2.21.The amplitude of an undamped system will not change with time.(T)2.A system vibrating in air can be considered as a damped system(T)3.The equation of motion of a single degree of freedom system will be the same whether the mass moves in a horizontalplane or an inclined plane.(T)4.When a mass vibrates in a vertical direction, its weight can always be ignored in deriving the equation of motion(F)5.The principle of conservation of energy can be used to derive the equation of motion of both damped and undamped systems(F)6.The damped frequency can be larger that the undamped natural frequency of the system in some cases(F)7.The damped frequency can be zero in some cases. (T)8.The natural frequency of vibration of torsional system is given by where k and m denote the torsional spring constant and the polar mass moment of inertia, respectively(T)9.Rayleigh’s method is based on the principle of conservation of energy(T)10.The final position of the mass is always the equilibrium position in the case of Coulomb damping. (F)11.The undamped natural frequency of a system is given by , where is the static deflection of the mass(T)12.For an undamped system, the velocity leads the displacement by . (T)13.For an undamped system, the velocity leads the acceleration by (F)14.Coulomb damping can be called constant damping(T)15.The loss coefficient denotes the energy dissipated per radian per unit strain energy.(T)16.The motion diminishes to zero in both underdamped and overdamped cases. (T)17.The logarithmic decrement can be used to find the damping ratio(T)18.The hysteresis loop of the stress –strain curve of amaterial causes damping(T)19.The complex stiffness can be used to find the damping force in a system with hysteresis damping(T)20.The motion can be considered to be harmonic in the cases of hysteresis damping(T)第三章3.21.The magnification factor is the ratio of maximum amplitude and static deflection(T)2.The response will be harmonic if excitation is harmonic(T)3.The phase angle of the response depends on the system parameter m, c, k, and ω(T)4.The phase angle of the response depends on the amplitude of the forcing function.(F)5.During beating, the amplitude of the response builds up and then diminishes in a regular pattern (T)6.The Q-factor can be used to estimate the damping in a system (T)7.The half power points denote the values of frequency ratio where the amplification factor falls towhere Q is the Q-factor. (T)8.The amplitude ratio attains its maximum value at resonance in the case of hysteresis damping(F)9.The response is always in phase with the harmonic forcing function in the case of hysteresis damping(T)10.Damping reduces the amplitude ratio for all values of the forcing frequency. (T)11.The unbalance in a rotating machine causes vibration(T)12.The steady state solution can be assumed to be harmonicfor small values of dry friction force(T)13.In a system with rotational unbalance, the effect of damping becomes negligibly small at higher speeds. A set is a collection of objects(T)第四章4.21.The change in momentum is called impulse (T)2.The response of a system under arbitrary force can be found by summing the responses due toseveral elementary impulses (T)3.The response spectrum corresponding to base excitation is useful in the design of machinery subject to earthquakes (T)4.Some periodic functions can not be replaced by a sum of harmonic functions (F)5.The amplitudes of higher harmonics will be smaller in the response of a system. (T)6.The Laplace transform method takes the initial conditions into account automatically (T)7.The equation of motion can be integrated numerically even when the exciting force is nonperiodic (T)8.The response spectrum gives the maximum response of all possible single degree of freedom systems (T_9.For a harmonic oscillator, the acceleration and displacement spectra can be obtained from the velocity spectrum. (T)第五章5.21.The normal modes can also be called principal modes (T)2.The generalized coordinates are linearly dependent (F)3.Principal coordinates can be considered as generalizedcoordinates (T)4.The vibration of a system depends on the coordinate system (F)5.The nature of coupling depends in the coordinate system (T)6.The principal coordinates avoid both static and dynamic coupling.(T)7.The use of principal coordinates helps in finding the response of the system (T)8.The mass, stiffness, and damping matrices of a two degree of freedom system are symmetric (T)9.The characteristics of a two degree of freedom system are used in the design of dynamic vibration absorber (T)10.Semi-definite systems are also known as degenerate systems (T)11.A semi-definite system can not have non-zero natural frequencies (F)12.The generalized coordinates are always measured form the equilibrium position of the body (F)13.During free vibration, different degrees of freedom oscillate with different phase angles (F)14.During free vibration, different degrees of freedom oscillate at different frequencies (F)15.During free vibration, different degrees of freedom oscillate with different amplitudes (T)16.The relative amplitude of different degrees of freedom ina two degree of freedom system depend on the natural frequency (T)17.The modal vectors of a system denote the normal modes of vibration (T)第六章6.21.For a multidegree of freedom system, one equation of motion can be written for each degree of freedom (T) /doc/db13674645.html,grange’s equation cannot be used to derive the equations of motion of a multidegree of freedom system (F)3.The mass, stiffness, and damping matrices of a multidegree of freedom are always symmetric (T)4.The product of stiffness and flexibility matrices of a system is always an identity matrix (T)5.The modal analysis of a n-degree of freedom system can be conducted using r modes with r < n (T)6.For a damped multidegree of freedom system, all the eigenvalues can be complex (T)7.The modal damping ratio denotes damping in a particular normal mode (T)8.A multidegree of freedom system can have six of the natural frequencies equal to zero (T)9.The generalized coordinates will always have the unit of length (F)10.The generalized coordinates are independent of the conditions of constraint of the system (T)11.The generalized mass matrix of a multidegree of freedom system is always diagonal (F)12.The potential and kinetic energies of a multidegree of freedom system are always quadratic functions (T)13.The mass matrix of a system is always symmetric and positive definite (T)14.The stiffness matrix of a system is always symmetric andpositive definite (F)15.The rigid body mode is also called the zero mode. (T)16.An unrestrained system is also known as a semi-definite system. (T)17.Newton’s second law of motion can always be used to derive the equations of motion of a vibrating system (T) 第七章7.21.T he fundamental fr equency given by Durkerley’s formula will always be larger than the exact value (F)2.The fundamental frequency given by Rayleigh’s method will always be larger than the exact value (T)3.is a standard eigenvalue problem (F)4.is a standard eigenvalue problem (T)5.Jacobi method can find the eigenvalues of only symmetric matrices. (T)6.Jacobi method uses rotation matrices. (T)7.The matrix iteration method requires the natural frequencies to be distinct and well separated (T)8.In matrix iteration method, any computational error will not yield incorrect results (T)9.The matrix iteration method will never fail to converge to higher frequencies. (F)10.When Rayleigh’s method is used for a shaft carrying several rotors, the static deflection curve can be used as the appropriate mode shape. (T)11.Rayleigh’s method can be considered to be same as the conservation of energy for a vibrating system (T)第八章8.21.Continuous systems are same as distributed systems. (T)2.Continuous systems can be considered to have infinite number of degrees of freedom. (T)3.The governing equation of a continuous system is an ordinary differential equation. (F)4.The free vibration equations corresponding to the transverse motion of a string, the longitudinal motion of a bar and the torsional motion of a shaft have the same form. (T)5.The normal modes of a continuous system are orthogonal. (T)6.A membrane has zero bending resistance. (T)7.Rayleigh’s method can be considered as a method of conservation of energy.(T)8.Rayleigh-Ritz method assumes the solution as a series of functions that satisfy the boundary conditions of the problem. (T)9.For a discrete system, the boundary conditions are to be applied explicitly. (T)10.The Euler-Bernoulli beam theory is more accurate than the Timoshenko theory. (F)第九章9.21.Vibration can cause structural and mechanical failures. (T)2.The response of a system can be reduced by the use of isolators and absorbers (T)3.Vibration control means the elimination or reduction of vibration (T)4.The vibration caused by a rotating unbalanced disc can be eliminated by adding a suitable mass to the disc (T)5.Any unbalanced mass can be replaced by two equivalent unbalanced masses in the end planes of the rotor (T)6.The oil whip in the bearings can cause instability in a rotor system (T)7.The natural frequency of a system can be changed by varying its damping (F)8.The stiffness of a rotating shaft can be altered by changing the location of its bearings (T)9.All practical systems have damping. (T)10.High loss factor of a material implies less damping (F)11.Passive isolation systems require external power to function (F)12.The transmissibility is also called the transmission ratio. (T)13.The force transmitted to the foundation of an isolator with rigid foundation can never be infinity (F)14.Internal and external friction can cause instability in a rotating shaft at speeds above the first critical speed (T)。
入学考试试题(A卷)(答案必须写在答题纸上)考试科目:微生物学科目代码：3819适用专业:水产资源综合利用一、简答题（共40分，每题10分）1、请你谈谈微生物的分类，并简述微生物分类鉴定有哪些方法2、叙述ELISA的基本实验过程，并解释其原理？3、大肠杆菌、酵母、乳酸菌在有氧和无氧条件下将丙酮酸分解生成的产物是什么？并列出其中关键的酶。
4、光能自养微生物、光能异养微生物、化能自养微生物、化能异养微生物的碳源和能源各是什么？二、问答题（共60分，每题15分）1、设计一种肉类发酵剂的筛选方案，简述其理由。
2、如何分析腐败变质鱼的原因菌，设计方案并解释原理。
3、如何从自然界中分离筛选出产蛋白酶活力较高、能在肠道内存活的乳酸杆菌?4、微生物污染食品的途径及其控制措施入学考试试题(B卷)(答案必须写在答题纸上)考试科目:微生物学科目代码：3819适用专业:水产资源综合利用一、名词解释（24分，每题3分）1、质粒：2．HMP途径：3．同型乳酸发酵：4．点突变：5．Continuous culture：6．有氧呼吸：7．抗体：8．营养缺陷型：二、简答与问题（共76分）1、简述微生物吸收营养物质的方式（12分）2、简述微生物分类的依据（12分）3、试述革兰氏染色的机理（12分）4、分析以下几对概念的区别（16分）4.1分生孢子与细菌芽孢4.2菌株与菌落4.3Complete medium和Minimal medium：4.4消毒与防腐：5、简述微生物在发酵乳制品主要风味物质形成中的作用（12分）6、简述酵母菌在以淀粉为主原料制造酒类的发酵原理及黄酒、啤酒和葡萄酒生产的基本工艺原理（12分）。
五邑大学（期末试题）院系：机电工程学院专业：机械工程年级： 12级研究生学号： 2111206011姓名：崔卫国机械振动考题1、如图所示两自由度系统。
（1）求系统固有频率和模态矩阵，并画出各阶主振型图形；（2）当系统存在初始条件⎥⎦⎤⎢⎣⎡=⎥⎦⎤⎢⎣⎡03.00)0()0(21x x 和⎥⎦⎤⎢⎣⎡=⎥⎦⎤⎢⎣⎡00)0()0(21x x 时，试采用模态叠加法求系统响应，并绘出相应曲线；（3）试合理确定k2和m2，使之构成无阻尼动力减振器。
（4）用任何一种语言编制计算程序，完成上述计算工作。
参数：m1=500kg, m2=200kg, k1=8000N/m, k2=3000N/m, F0=350N, ω=0.8解：（1）由题意及图所示可知：这是一个动力减震器问题。
1m 1k 组成的系统为主系统；2m 2k 组成的附加系统为减振器。
故可知这个组合系统的振动微分方程为：()11121221222122sin 0m x k k x k x F wt m x k x k x ⎧++-=⎪⎨-+=⎪⎩ ① 设其解为：11sin x X wt = 22sin x X wt = ② 又因为由②可得：211sin x X w wt =- 222sin x X w wt =- 把②代入方程①中可得：()()212112212112220k k w m X k X F k X k w m X ⎧+--=⎪⎨-+-=⎪⎩ 故系统的特征值问题为：2111212222220X F k k w m k X k k w m ⎡⎤+--⎡⎤⎡⎤=⎢⎥⎢⎥⎢⎥--⎣⎦⎣⎦⎣⎦ ③ 特征方程为：2121222220k k w m k k k w m +--=-- ④由④可得：()()2222212120kw m k k w m k -+--=⇒222412*********k k k w m k w m k w m w m m ---+= ⑤ 把1k 2k 1m 2m 的值代入⑤式可得：42372400w w -+= ⑥21223720.22378.388223720.223728.61192w w -⎧==⎪⎪⎨+⎪==⎪⎩⇒ 12 2.89625.3490w w =⎧⎨=⎩计算对应二个固有频率的固有振型。
