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sliding
相关语句
  滑动
    Friction Vibration (Ⅱ) Relation between Dynamic Friction and Sliding Velocity
    摩擦振动(二) (二)动摩擦力与滑动速度的关系
短句来源
    The Study of Lubricated Sliding Wear Behavior and its Mechanism of Steel
    润滑条件下钢的滑动磨损特性及其机理的研究
短句来源
    Evaluation of Tribological Behaviour of a-Al_2O_3 Ceramic under Dry Sliding Conditions
    α-Al_2O_3陶瓷材料在无润滑滑动条件下摩擦学特性的评定
短句来源
    INVESTIGATION ON THE RELATIONSHIP BETWEEN SLIDING SPEED AND SOIL-METAL FRICTION
    金属-土壤摩擦阻力与滑动速度关系的研究
短句来源
    Mechanism of the Noise results from Sliding Friction
    滑动噪声的机理探索
短句来源
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  “sliding”译为未确定词的双语例句
    The Research of the Intelligent Virtual Maintenance Technology about the Wear of Sliding Bearing Based on Internet
    面向INTERNET的滑动轴承磨损智能虚拟维护技术的研究
短句来源
    Investigation of the Mechanism of Voltage-Controlled Friction of Metal/Ceramic Sliding Couples in Aqueous Solutions
    水溶液中金属/陶瓷摩擦副电控摩擦效应的机理研究
短句来源
    Optimum Design of Hydrodynamic Sliding Bearings (Ⅲ) Mathematical Model of Optimum Design
    流体动压滑动轴承优化设计 (三)优化设计的数学模型
短句来源
    THE DESIGN PROGRAM of DEYNAMIC PRESSURE RADIAL SLIDING BEARING
    动压径向滑动轴承设计计算程序
短句来源
    New structures and Frictional Characteristics of Plastic Sliding Bearings
    塑料滑动轴承的新结构及摩擦特性
短句来源
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  sliding
Adaptive fuzzy sliding mode control of Lorenz chaotic system
      
By using the exponential reaching law technology, a sliding mode controller was designed for Lorenz chaotic system subject to an unknown external disturbance.
      
Furthermore, to eliminate the chattering resulting from the discontinuous switch controller and to guarantee system transient performance, a new adaptive fuzzy sliding mode controller was designed.
      
Then the sliding average least squares (SALS) method was adopted to determine the mass, damp, and stiffness of the remote environment and use this information to amend the dynamic model of the environment.
      
A sliding mode perturbation observer (SPO) is designed to estimate unmeasurable states and system perturbations that involve system nonlinearities, disturbances and unmodelled dynamics.
      
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Briefly introducing the principle of operation of the sliding-vane rotary flowmeter,a reasonable design of the chamber profile in this kind of flowmeter is suggested in this paper with the intention of meeting such technical requirements as higher metering accuracy and less counting loss,wider metering range,less pressure loss,lower vibration and noise,steady rotation and less metering error due to the viscous property of the fluid metered.For the reason given above,the cycloid,taken as a transition curve...

Briefly introducing the principle of operation of the sliding-vane rotary flowmeter,a reasonable design of the chamber profile in this kind of flowmeter is suggested in this paper with the intention of meeting such technical requirements as higher metering accuracy and less counting loss,wider metering range,less pressure loss,lower vibration and noise,steady rotation and less metering error due to the viscous property of the fluid metered.For the reason given above,the cycloid,taken as a transition curve of the chamber profile connecting two arcs with different curvature radii,is a substitute for the elliptic curve proposed in an earlier paper[1],thus preventing the impulse due to the radial acceleration caused by the elliptic curve.The theoretical and practical formulas of the chamber profile are shown as in formulas (6),(9) and (11) respectively,and the oscillating angle (pressure angle)λ and the minimum width of sliding-vane are also given.Finally,the possibilities of the smooth motion of sliding-vane and of the use of form milling to manufacture the chamber profile are also discussed.

本文简要论述了刮板式流量计的工作原理及其特点,论证了用摆线作为腔体型线的过渡曲线的合理性,并给出计算腔体的理论与实际型线方程。讨论了滑片运动的平稳性以及根据腔体型线的形成原理用“创成法”加工腔体型线的可能性。

In this paper,mathematical derivation of contact lines and relative principal curva-tures of cylindrical gears are presented.These equations may be taken as a basis foranalysing inproving the prevailing tooth profile.Also is given a theoretical basis for contrasting tooth profiles now available andfor researching new tooth profiles.The following symbols are used in this paper:x,y——Cartesian coordinates of basic rack(see Fig.1)(?——Polar angle of pitch point(see Fig.2)r——Distance of pitch point from point of tooth...

In this paper,mathematical derivation of contact lines and relative principal curva-tures of cylindrical gears are presented.These equations may be taken as a basis foranalysing inproving the prevailing tooth profile.Also is given a theoretical basis for contrasting tooth profiles now available andfor researching new tooth profiles.The following symbols are used in this paper:x,y——Cartesian coordinates of basic rack(see Fig.1)(?——Polar angle of pitch point(see Fig.2)r——Distance of pitch point from point of tooth profiles(see Fig.2)θ——Angle of normal line(see Fig.2)z——Number of teethX,Y,Z——Moving coordinated axes of tooth surfaces(see Fig.3)X_0,Y_0,Z_0——Fixed coordinates of tooth surfacesε——Rotating angle of transverse sectionβ——Helix angle of helical gears(?)——Rotating angle of gearsm——ModuleL——Length of contact linek——Relative principal curvature(?)——Tooth normal vector(?)——Tangential vector of contact line(?)——Unit vectors of fixed coodinates(?)——Angular velocity vectorω——Angular velocity(?)——Velocity vectors of tooth profiles(?)——Sliding velocity vectorσ——Sliding ratioi_(12)——Velocity ratioA_0——Center distancea_0——Pressure angleβ_i——Helixangle at base circler_0——Radius of circuler profileC——Distance of centre from pitch line K——Relative principal curvature factor(?)——Specific value of relative principal curvature factor and length of contact lineIf the profile equation of basic rack is known,the following equation will givethe contact line of cylindrical gearsX_(01)=m((z_1/2)secβ_0+y)Y_(01)=-myy'cosβ_0 (17)Z_(01)=mctgβ_0[(z_1/2)(?)_1-(xsecβ_0+yy'cosβ_0)]where y'=dy/dxThe equation for relative principal curvature is:k=-((z_1+z_2)[(1+y′~2+yy″)~2ctg~2β_0+(1+y′~2)])/2msecβ_0(1+y′~2)~(3/2){z_1/2±|ycosβ_0[1+(y′~2+yy″)cos~2β_0]|}sin~2β_0/z_2/2(?)|y cosβ_0[1+(y′~2+yy″)cos~2β_0]|}Where y″=d~2y/dx~2In circular conjugate gears,formula(17)can be written asX_(01)=m[z_1/2secβ_0±(r_0cosθ-c)].Y_(01)=(?)m(r_0sinθ-ctgθ)cosβ_0 (43)Z_(01)=mctgβ_0{z_1/2(?)_1(?)[(r_0~2-c~2)~(1/2)secβ_0-(r_0sinθtg~2β_0+ctgθ)cosβ_0}Fig.4 shows some contact lines of the circular conjugate gears.The equation for length of contact line of the circular conjugate gears isL=mr_0(θ_a-θ_b)η (50)where η is length factor of contact line(see Table 1)The equation for relative principal curvature of the circular conjugate gears is(?)where is specific value of the involute gears,is specific value of thecircular conjugate gears(c=0).The following values are respectively:β_0=11°28′42″ (?)≈6β_0=25°(?)≈2.5

本文导出了圆柱齿轮的接触线与相对主曲率的一般方程式,为分析比较现有的圆柱齿轮齿廓和探索新齿廓提供了一个理论依据。

Outlined in this article are the methods of designing of the geared- bar mechanism with brief dwell for sliding driven members, including the determination of the length of the coupler, the calculation of the stroke of the slider and the fixed-carrier train ratio for the planetary gear trains. The author is also discussing the maximum offset of the driven slider to the dwelling point.

本文讨论了移动从动件间停的齿轮连杆机构各参数的设计方法:包括确定连杆长度的计算公式、组成行星机构的转化机构传动比范围、从动件的行程计算和从动件对停点位置的最大偏距等。

 
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