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不旋转     
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  non rotation
     To analyze technology difficulty of producting 40(18×7:7×7+7×7-7×7-1×17 S) multilayer strand non rotation ropes. The design and production of such structure rope are introduced.
     分析 4 0 (18× 7:7× 7+7× 7- 7× 7- 1× 17S)多层股不旋转钢丝绳生产技术难度 ,介绍该结构钢丝绳设计和生产过程
短句来源
     To introduce the production experience of non rotation multiple layer strand wire rope taking 34×7+IWS? I 12? mm and 14?
     以 34× 7+IWS— 12mm、 14mm为例介绍多层股不旋转钢丝绳的生产经验。
短句来源
     and 34×7 multilayer strand non rotation ropes have such structure and technical characteristics as strand having the same structure, stranding layer ropes according to equal spiral angle.
     17× 7类、34× 7类多层股不旋转钢丝绳具有组绳股结构相同、层绳按照等捻角分层捻制的结构特点和工艺特点。
短句来源
     To introduce structure and process design of horizontal adjustable predeformation apparatus according to production require of FNR series multilayer stands non rotation ropes.
     根据FNR类多层股不旋转钢丝绳的生产要求 ,对卧式可调式预变形器进行结构和工艺设计。
短句来源
     To introduce the characteristics of structure design for non rotation wire rope with tier strands,give many calculating formulas,put forward the main points for attention in production and the methods for testing wire rope
     介绍多层股不旋转钢绳结构设计的特点,给出多个计算公式,提出生产时的注意要点和钢绳的测试方法。
短句来源
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  nor rotating
     To introduce basic instance of trial manufacture SWAGED4×39S+FC nor rotating wire rope by means of forging method. The wire rope structure,twisting parameters and forging scheme are confirmed by studying the production process and practicality sample of wire rope with four sector strands at home and abroad.
     介绍采用锻打法试制SWAGED4× 39S +FC不旋转钢丝绳的基本情况 ,通过研究国内外四股扇形钢丝绳生产工艺和实物样品 ,确定钢丝绳结构、捻制参数和锻打技术方案。
短句来源
     It is indicated by production practice that the nor rotating wire ropes with 1 770 MPa grade and 13~28 mm are manufactured by adopting ZS twisting,selecting the twisting multiples of strands and rope to be from 6.70 to 7.00 and from 8.40 to 9.00 respectively,controlling the compression ratio of forging to be at about 10%, which can meet the technical requirements no matter breaking force or toughness targets of the steel wire of dismantled strand.
     生产实验表明 ,采用ZS捻 ,钢丝绳股、绳捻距倍数分别在 6 .70~ 7.0 0 ,8.4 0~ 9.0 0范围内选取 ,锻打压缩率控制在 10 %左右 ,可生产出强度级别 1770MPa的 13~2 8mm不旋转钢丝绳 ,其破断拉力和拆股钢丝韧性指标满足相应技术要求
短句来源
  non-rotation
     Production of Multilayer Strand Non-Rotation Ropes
     多层股不旋转钢丝绳生产
短句来源
  nor-rotation
     Nor-rotation Property Analysis and Structure Improvement of Multi-strands Steel Wire Rope
     多股钢丝绳不旋转性能分析及结构改进
短句来源
     The theory and practical use show that multi-strands wire rope have more advantages than the single-strand wire rope on nor-rotation property, but have still more defects.
     理论计算和实际使用效果显示,多股钢丝绳虽然比普通单层股钢丝绳在不旋转性能上有较大的优越性,但仍然存在较多缺陷。
短句来源

 

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      non-rotation
    N-PEPM (5 mm × 12 mm, 120 mT non-rotation) was also applied as control.
          
    Volvulus of the ascending colon: An unusual complication of non-rotation of the midgut
          
    A case of non-rotation of the bowel is presented wherein volvulus of the colon occurred causing acute obstruction.
          
    This type of volvulus is distinctly different from midgut volvulus and is a rare complication of the anomaly of intestinal rotation and fixation known as non-rotation of the bowel.
          
    Midgut non-rotation with a large, dumb-bell-shaped, abscessed, air-containing right paraduodenal hernia in early childhood
          
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      non rotating
    The dissociation energy for a non rotating molecule was determined to be D0=0·121±0·01 volts.
          
    The motion of axisymmetric non rotating black holes is discussed using the properties of Weyl solutions.
          
    The relativistic interior dynamics of a spherically symmetric, non rotating star composed of an elastic material is analyzed.
          
    A device for sensing a condition of a non rotating pneumatic tyre mounted on a rim is described.
          
    This is in particular the case in head-on collisions of non rotating spheres.
          
      其他


    In this paper the experimental methods for determining the critical speeds of rotor systems are investigated. The methods reviewed here are the peak amplitude method and those based on the charateristics of critical speeds, such as the 90 degree phase lagging, and the rapid change of phase angle.The peak amplitude method commonly used will introduce significant error in practice if the shaft is out of round or initially bent, or it is observed under the condition of acceleration. Even if the tests are performed...

    In this paper the experimental methods for determining the critical speeds of rotor systems are investigated. The methods reviewed here are the peak amplitude method and those based on the charateristics of critical speeds, such as the 90 degree phase lagging, and the rapid change of phase angle.The peak amplitude method commonly used will introduce significant error in practice if the shaft is out of round or initially bent, or it is observed under the condition of acceleration. Even if the tests are performed at constant speeds the undamped critical speed will still be much higher in case of heavily damped rotors, while the method based on the 90 degree phase shift is more suitable for these cases.For the lightly damped rotors, which are just the cases for manypractical rotors, the method based on the rapid change of phase angle when passing through critical speed is more applicable, since the rotors may be more safely tested with accelaration which does not affect the measured results of critical speeds by using this method.A modified Nyquist plotting procedure is presented, in which a trial weight is put on the node section of the higher order mode shape, and necessary tests are made only at some speeds near the critical. The vibration vectors without error are then obtained and a circular polar plot can be made. With the aid of the plot the critical speed can be calculated in accordance with the fact that the increment of speed is nearly proportional to the increment of phase lagging angle in the vicinity of a critical speed.It is suggested that the first critical may be experimentally determined at lower speeds for the rotors with assymmetric stiffness, these are the cases for many real rotors. The sub-critical is measured in this method and its double is then the first order critical speed. It is known that at sub-critical the vibration frequency is twice the speed, while at critical the vibration frequency is equal to the speed. Therefore, it is possible to distinguish the sub-critical from the first critical by comparing the measured frequency with speed. This method is considered as a safer and simpler method.Finally the feasibility of the method to determine the critical speeds in the static states of the rotors is discussed.

    本文研究转子系统临界转速的实验测定法。分析、评述了振幅峰值法和根据滞后相角为90°及其在临界附近急速变化(“质心转向”)现象确定临界转速的方法。包括将用于柔轴平衡的振型圆法改变用来测定临界转速的方法。提出一种简便安全的低速测定临界转速的方法。最后论述了转子不旋转测定临界转速的方法。用物理慨念和简单数学公式阐明所依据的原理,指出了各种方法的优、缺点和适用范围。

    Author, according to the principles of thc dynamics, analyses stock on the chute. There are six forces effecting it: gravity, inertial centrifugal F, reactionary force of chute to stock N, friction F_f, inertial Coriolis'S force F_k and the chute exerts two forces on the stock. Thus deriving unified stock distribution equation of expressed stock distribution which can be applied to both the rotative distributor and nonrotative distributor: ? This equation indicate effect of stock distribution of the following...

    Author, according to the principles of thc dynamics, analyses stock on the chute. There are six forces effecting it: gravity, inertial centrifugal F, reactionary force of chute to stock N, friction F_f, inertial Coriolis'S force F_k and the chute exerts two forces on the stock. Thus deriving unified stock distribution equation of expressed stock distribution which can be applied to both the rotative distributor and nonrotative distributor: ? This equation indicate effect of stock distribution of the following ll variables: length of the chute ι_υ, angle of the chuteβ, rotation speed of chute ω, coefficient of friction μ, initial speed of stock C_o, weight of stock Q, grain size and shape of stock (about s), density of gas γ, gas vclocity v and depth of stock line h. Change of one or several variables must lead to change of the stock distribution. These change can be quantitatively calculated by equation(69). Equation(69) is not only suitable to rotative distributor of chute, but also suitable to nonrotative distributor of bell. When ω=0, equation (69) changes into the stock distribution equation of bell type.

    作者从动力学人手,分析炉料在溜槽上的受力作用,计有六个力:重力;惯性离心力F;溜槽对炉料的反作用力N;摩擦力F_f;惯性Coriolis力_k和因溜槽旋转而产生的侧向摩擦力.导出旋转与不旋转的布料器都适用的、描述炉料分布的统一布料方程:?这个方程全面地反映了溜槽长度l_0、溜槽角度β、溜槽转速ω、炉料初速度C_0、炉料重量Q、炉料形状和粒度(关系s)、煤气重度γ、煤气速度ν、摩擦系数μ和料线深度h等11个变量对炉料分布的影响.任何一个或几个变量改变,都会引起炉料分布的改变,这些变动可由(69)式定量的计算出来;(69)式不仅对转动的溜槽布料器适用,它也适用于不转动的装料设备.当ω=0时,方程(69)变成料钟型布料方程.

    According to the national standard ( GB1806-79 ) for oil drilling rig and characteristics of rig load capacity, on the basis of using plastic design concept and selecting a certain safety coefficient for static strength, the writer discusses the strength analysis and calculation for the tensile parts and non-rotary axle parts ( including a beam, a curved beam and shear ) in the rig hoisting equipment, as a result, presents the safety coefficient of static strength requisite for assuring fatigue strength. After...

    According to the national standard ( GB1806-79 ) for oil drilling rig and characteristics of rig load capacity, on the basis of using plastic design concept and selecting a certain safety coefficient for static strength, the writer discusses the strength analysis and calculation for the tensile parts and non-rotary axle parts ( including a beam, a curved beam and shear ) in the rig hoisting equipment, as a result, presents the safety coefficient of static strength requisite for assuring fatigue strength. After analysing: the concrete representation which is convenient for designers to use it during designing and calculating is given as well.

    本文根据钻机国家标准(GBl806—79)和钻机承载的特点,利用极限设计的概念,作者在选择一定的静强度安全系数的基础上,讨论了钻机提升设备中的受拉伸零件和不旋转的轴类零件(包括直梁、曲梁、剪切)的强度分析和计算,并给出了为保证疲劳强度所需的静强度安全系数。通过分析,本文给出了具体的表达式,便于设计计算时使用。

     
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