圆频率

词组短语

circular frequency

与圆频率相关的网络例句 [注：此内容来源于网络，仅供参考]

Two-dimensional finite difference time domain simulation results show that, in a wide angle range (about 20 degrees), in a normalized circular frequency range of , the transmission intensity can reach over 98% for both TE and TM polarization.

二维有限时域差分模拟结果显示，在较宽的角度范围内（约20度），约化圆频率处在范围内，分束器对TE和TM偏振光的透射强度都能达到95%以上。

This article first antenna, microstrip theory, the circular polarization technology, the theoretical discussion, in this based on the microstrip antenna of circular polarization method - corner square microstrip antenna, and has done a design simulation , and then do the design and further research to improve and eventually get a resonant frequency (S11 reflection coefficient corresponding to the minimum frequency) for the 1.5GHz and 1.43GHz, the frequency of circular polarization for the 1.46GHz, S11 is less than -10dB relative bandwidth, the VSWR is less than 2 is about 8.8% relative bandwidth, axial ratio less than 3dB relative bandwidth of about 2.2% of the right circular polarization microstrip antenna design case, which proved very good the circular polarization microstrip antenna theory, also fully confirmed by a square corner design is a practical program, and select the appropriate regulation of sticks is indeed able to improve the performance of the antenna.

本文先对天线、微带理论、圆极化技术等进行了理论论述，在此基础上，提出圆极化微带天线的实现方法——切角方形微带天线，并对此做了设计仿真，后又对这一设计方案做了改进及进一步研究，最终得到一个谐振频率（反射系数S11 的最小值所对应的频率）为1.5GHz和1.43GHz，圆极化频率为1.46GHz，S11 小于-10dB 的相对带宽、驻波比小于2 的相对带宽约为8.8%，轴比小于3dB 的相对带宽约为2.2%的右旋圆极化微带天线的设计案例，从而很好的印证了圆极化微带天线理论，也充分证实了切角方形是一种切实可行的设计方案，而选取合适的调节枝则确能提高天线的性能。

The following are the expressions for the mean pressure set up at the detection plate and for the time of the signal to progagate from the radiator to the detector:这里是1个公式,省略） where Re is the real part of the expression appearing within the braces, 0 is the density of the medium, vo is the amplitude of the vibrational velocity, c is the speed of sound in the medium, d2 = I +(r/zcos 8, z is the distance between the emitting and receiving plates, B is the angle between the axis of the acoustic channel and the axis of the tube, r = vro/c, v is the flow speed of the fluid, d is the diameter of the pipe, m is the circular frequency, k is the wave number, where a is the radius of the plate (this is taken as the same for the emitting and receiving plates for simplicity, but there is no difficulty in discussing plates differ~mg in radii),,~ is the vibrational frequency of the emitting plate, and The triple sums in the expressions for N~ and N2 may be neglected if the flow speed is low, since the contributions for these become negligible.

以下的表情为代表的压力设置在检测板甲，手持骑枪和时间的信号 progagate从散热器排出到检测器(这里是1个公式、省略)。在什么地方才是真正的出现在背带，表现为0密度的吗当时的媒介的振幅振动速度、c是声音的速度中、d2 =我+ r / z，8、z是距离的发射和接收板、B之间的角度对声信道和轴轴管，r = vro / c，v的流体的流动速率公式，d 管直径的圆频率，m，凯西是波数公式* n，一个是半径的板(这是作为相同的发射和接收吗为了简单，但板板是毫无困难地讨论不同半径)、镁-，~的振动频率的发光，。总结了三倍的表达方式和N2 ~能忽略的流量速度低，因为这些变得微不足道的贡献。

The following are the expressionsfor the mean pressure set up at the detection plate and for the time of the signal toprogagate from the radiator to the detector:这里是1个公式,省略） where Re is the real part of the expression appearing within the braces, 0 is the density ofthe medium, vo is the amplitude of the vibrational velocity, c is the speed of sound in themedium, d2 = I +(r/zcos 8, z is the distance between the emitting and receiving plates, B is the angle between the axis of the acoustic channel andthe axis of the tube, r = vro/c, v is the flow speed of the fluid, d is thediameter of the pipe, m is the circular frequency, k is the wave number,where a is the radius of the plate (this is taken as the same for the emitting and receivingplates for simplicity, but there is no difficulty in discussing plates differ~mg in radii),,~ is the vibrational frequency of the emitting plate, andThe triple sums in the expressions for N~ and N2 may be neglected if the flow speed islow, since the contributions for these become negligible.

以下是表达式平均压力为定于检测板和为信号时间progagate从散热器到探测器：（这里是1个公式，省略）假如再是出现在大括号表达式的实部，0是密度中期，沃是速度的振动幅度，C是健全的速度中，D2中=我+的导向8，z是对之间的距离发射与接收板，B是声之间的通道轴角该管的轴，R =中心内大多分为/荤，v是流体的流动速度，，D是管道直径，m是圆频率，k是波数，的其中一盘是半径（这是为重点，同样的发射与接收为le简单板，但没有讨论板的困难，在半径不同毫克），，是发光板振动频率，和在N的表达式的三重总结和N2可以忽略，如果流速低，因为这些变得微不足道的贡献。

What Coriolis force contribute to the frequency is analysised later.

并分析了Coriolis效应对潮波圆频率的贡献。

The effect of tribology factors on bearing vibration is studied experimentally. AR model and WPT are used to processing the normal arid abnormal signals. The results are as follows:1. The vibration of ball bearings is caused by the tribology action of contact pairs of ball and ring races and has the essential of tribo-dynamics. Any factors affecting the tribology characteristics of contact pairs will affect vibration and noise of bearings consequently.2. Vibration characteristics of bearing keep almostly unchanged with the increasing of axial load expecting the increasing of nature frequencies. When radial load increasing with axial load unchanged, nature frequencies keep unchanged but some new vibration peaks appears in the spectrum.3. Vibration amplitudes are damped and nature frequency are enhanced with sufficient lubrication. Vibration and noise of bearings increase obviously and roar can happen and the contact surfaces scratch slightly under insufficient and unclean lubrication state. Bearing will be disabled in a few minutes without any lubrication.4. Bearing vibration is unstable under low speed. With the speed increasing, the vibration become stable and natural frequencies increase slightly but the amplitudes increase apparently.5. Bearing vibration can be excited only by some harmonics ofwaviness without lubrication and by all harmonics with lubrication based on the theoretical analysis.6. The nature frequencies of ball bearings decrease with the increasing sizes. When international clearance increasing, nature frequencies decrease in radial and increase in axial and angular and the amplitudes increase in radial and decrease in axial and angular. When the number of balls increasing, nature frequencies increase and amplitudes decrease. When the pitch diameter increasing, axial nature frequency increase and others nearly keep no change. When outer race groove curvature radius increasing, nature frequencies increase in radial and decrease in axial and angular and amplitudes keep no change in radial and increase in axial and angular. When inner race groove curvature radius increasing, nature frequencies decrease and amplitudes increase.7. The distortion in amplitude and frequency components of bearing vibration signals picked up by the present probe measurement method is founded and right conclusions cannot be achieved by the signals. When accelerometer is rigidly screwed with steel stud onto a flat outer surface of a ball bearing, vibration signal can be got without distortion and the reliability of research on bearing vibration is assured.8. AR model is suitable for large samples of bearing vibration signals, square root of length of samples can be used as the upper limitation of order determination and the FPE order selection criterion is effective. Many advantages of AR spectrum are founded over the classical based on FFT.9. Time-Frequency analysis is necessary for abnormal noise of ball bearings. WPT overcomes the principle shortcomings of STFT and proved to be a best tool to process the abnormal signals.

理论分析和试验研究表明： 1球轴承振动是钢球—滚道接触副中的各种摩擦学作用引起的，具有摩擦动力学的本质，任何对接触副的摩擦学特性有影响的因素都将对球轴承的振动和噪声特性产生影响； 2中心轴向载荷作用下，载荷增大使球轴承的固有振动频率升高，载荷越大同样的载荷增幅引起的频率升幅减小，足够大的中心轴向载荷作用下载荷的变化对球轴承振动的频率特性不会产生明显的影响； 3轴向和径向联合载荷作用下，径向载荷不大时球轴承振动的固有频率基本不变，但是可能引起变刚度激励的非线性振动，出现新的频峰，过大的径向载荷将使部分钢球脱离接触，使球轴承的振动和噪声呈现不稳定状态； 4润滑对球轴承的振动和噪声特性有重要的影响，良好的润滑对振动有明显的抑制作用，润滑不充分时，振动和噪声的水平会有明显增高，一定条件下还会激发接触副中的谐振，发出啸声，造成接触表面的伤害，无润滑干接触时，短时的运转就会损伤接触副表面，使振动和噪声迅速增大，并随时可能引发严重的磨损和卡滞失效；接触副润滑良好时，油膜的"刚化效应"使球轴承振动的固有频率有所提高，润滑剂中含有弥散性污浊时，振动的幅度总体升高，但弥散性污浊不会改变球轴承振动的频率特性；浙江大学博士学位论文：球轴承振动的研究 5低速时，球轴承振动的基本特征呈现不稳定状态，随着转速的提高，球轴承振动的频率特性趋于稳定，固有频率频峰升高； 6理论分析表明，干接触时钢球和滚道表面波纹度的某些谐波分量能激励球轴承的振动，振动的幅值与谐波幅值成正比，实际球轴承中钢球的分布不可能完全均匀，波纹度的激励作用会随时发生；润滑接触的分析表明，波纹度的任意谐波分量均能激励球轴承的振动； 7球轴承的几何和结构参数分析表明，球轴承尺寸越大，径向、轴向和角振动的固有频率越低；钢球中心圆直径增大，球轴承的径向和轴向振动的固有频率基本不变，角振动的固有频率有所上升，振动的幅频特性基本不变；径向游隙加大使球轴承的径向振动固有频率降低，轴向和角振动的固有频率有所升高，径向振动幅频特性的幅值升高，而轴向和角向降低；钢球的数量增多使球轴承振动的固有频率上升，幅频特性的幅值下降，径向振动的幅值下降最为明显；外圈沟曲率半径系数增大使球轴承径向振动的固有频率升高，轴向和角振动的固有频率降低，径向幅频特性基本不变，轴向和角向幅频特性幅值升高；内圈沟曲率半径系数增大使径向、轴向和角振动固有频率均下降，振动幅频特性的幅值均有升高； 8试验对比表明，传感器采用探针式安装时，由于探针接触副接触特性的影响，钡(量得到的球轴承振动信号有失真，采用专门设计和制作的试验球轴承，以固定式安装加速度计，首次测量得到了球轴承振动的真实信号，通过对振动信号的分析，验证了球轴承振动的理论模型； 9)基于时间序列分析的AR模型适用于大样本球轴承振动信号的分析，以样本长度的均方根值作定阶上界，FPE做判阶准则，给出的AR谱光滑，频率分辨率高，是球轴承振动分析的简便而可靠的手段； 10以时频域分析的小波包变换分析球轴承异音信号能够比较好地定位和聚焦异音发生的时间，时间间隔，频率范围，同样是球轴承振动分析的可靠的手段，可用作球轴承故障诊断技术。

A forced vibration is the oscillation of a body under the action of an external disturbing force.

强迫振动：在外加激振力作用下的振动。H—力幅；—激振力的圆频率；—激振力的初相位。

A set of complex Morlet wavelet are applied on projection slice of each direction to decompose each projection into several frequency channels,the average and variance extracted are computed in each frequency channel,and then linear regression model is employed to computer realationship feature between frequency channels.1-D DFT is applied to features and the amplitudes of Fourier coefficient are selected as features,then the extracted features are rotation invariant.

该算法是将一定大小的图像进行二维傅里叶变换；其次在变换后的图像中央选择一个圆盘区域，并在方向［0°，180°］内进行等间隔角度频率抽样，实现方向分解，使用一组复Morlet小波对每个方向上的映射切片进行小波变换，从而实现多通道频率分解；在各个频率通道中计算均值和方差作为特征，并利用线性回归模型计算频率通道之间的关系特征；将特征沿方向进行一维傅里叶变换并取其幅值，从而得到旋转不变性特征。

The results show that the fluctuation of the light field can be squeezed periodically. The initial occupancy of the BEC atomic levels has great influence on the squeezing properties of light and the period of oscillation of the squeezing is relating to the circle frequency of the light.

结果表明：光场在与原子BEC相互作用过程中呈现周期性压缩， BEC原子能级的初始占据率对光场的压缩特性具有重要影响，光场压缩的振荡周期与光场圆频率有关。

The fre-quency equations are derived according to stress match, consid-ering gear as a thin bar and adopting exponential horn. Then the influences of vibration of transformer which consists of horn and gear are explored, which come from the length of horn and the machining frequency. It has been discovered that the reso-nance frequency of the horn is the detune one of transformer and the resonance frequency is not same as one of horn, which provide theoretical rules for transformer design.

鉴于此，根据应力耦合，将齿轮作为圆盘，采用指数型变幅杆，推导频率方程，对变幅杆的设计长度和变幅器振动频率进行数值分析，发现变幅杆的共振频率恰好是变幅器的失谐频率，变幅器的共振频率与变幅杆的固有频率也不相同，这能够为超声珩齿变幅器的设计提供理论依据。

与圆频率相关的网络解释 [注：此内容来源于网络，仅供参考]

cyclotron angular frequency：回旋加速器角频率

"cyclotomic polynomial","分循环多项式,分圆多项式" | "cyclotron angular frequency","回旋加速器角频率" | "cyclotron angular precession frequency","回旋加速器角进动频率"

circular frequency：角频率

circular domain 圆形域 | circular frequency 角频率 | circular functions 圆函数

circular frequency：圆频率

circular cofferdam 圆形围堰 | circular frequency 圆频率 | circular pan mixer 圆盘式搅拌机

circular frequency：角频率,圆频率

1223. circular flue 圆形火筒(炉胆) | 1224. circular frequency 角频率,圆频率 | 1225. circular function 圆函数,三角函数

natural circular frequency：自然圆频率

natural cementing material 天然胶结材料 | natural circular frequency 自然圆频率 | natural clay 天然粘土

natural circular frequency：自然圆频率;自然周频

函数的自然边界 natural boundary of a function | 自然圆频率;自然周频 natural circular frequency | 自然方程 natural equation

wave circular frequency：波浪圆频率

波速 wave celerity | 波浪圆频率 wave circular frequency | 距波高度 wave clearance

average circular frequency：平均圆频率

频率Frequency | 平均圆频率average circular frequency | 拍beat

circular error probability：圓形公算誤差;圓機率誤差

"circular dispersion","圆形散射" | "circular error probability","圆形公算误差;圆机率误差" | "circular frequency","圆频率"

sum of circular vector：圆矢量和

sum frequency 和频,总频率 | sum of circular vector 圆矢量和 | sum of phasor 相量和