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seal pressure     
相关语句
  密封压力
     Seal Pressure of Hydraulically Expanded Tube to Tube Sheet Joints
     液压胀接接头的密封压力
短句来源
     The section structure of the product was designed to muli layer sealing lip scattered in internal was diameter and a bowshaped structure of the centre,thus there was large static seal pressure as installing.
     主体橡胶选用三元乙丙橡胶 ,产品截面结构设计成内径分布多层密封唇、中央呈弓形结构 ,安装时静密封压力大。
短句来源
     The relationship of these major parameters such as groove numbers and spiral angle to seal pressure is revealed and the optimized result is obtained.
     分析了影响密封性能的主要设计参数如螺旋角α,槽数n等对密封压力的影响规律 ,得出了优化结果 .
短句来源
     The present st udy shows that there is a critical seal pressure which is only related to the co mpression ratio and the friction coefficient, but does not depend on the radius of the elastomer ring.
     分析结果表明,临界密封压力只与橡胶圈的压缩量和密封面摩擦系数有关,与橡胶圈截面半径无关。
短句来源
     According to the magneto-rheological effect of magnetic fluid,the formula of seal pressure for magnetic fluid was presented. The yield stress of magnetic fluid was tested,it shows the result of the formula is same as the experiment data.
     根据磁性液体的磁流变效应,推导出磁性液体密封压力的计算公式,通过测试磁性液体的屈服应力,验证了该公式。
短句来源
  低压封装
     The Measurement of Internal Moisture Content and Low Seal Pressure Limit
     内部水汽含量检测技术和低压封装限制
短句来源
  封压力
     Retrofit of Shaft Seal Pressure Control System of 200MW Turbine
     200MW汽轮机轴封压力控制系统改造
短句来源
     In view of turbine oil's cleanliness degradation in many power plants, analysis has been carried out from aspects of equipment's manufacture, installation, repair and shaft seal pressure etc. , the causes are found, and concrete remedial methods and preventive countermeasures are given.
     针对多数电厂汽轮机油清洁度下降问题 ,从设备制造、安装、检修、轴封压力等方面进行了分析 ,找出了原因 ,并给出了具体的处理办法及防止对策
短句来源
  “seal pressure”译为未确定词的双语例句
     The airway seal pressure was(26±4)cm H_2O with PLMA and(16±3) cm H_2O with SLMA.
     呼吸道密封压SLMA组为(16±3)cm H_2O,PLMA组为(26±4)cm H_2O。
短句来源
     The time required for insertion of PLMA and IT was averaged 24.2 and 22.7,respectively the airway seal pressure in group PLMA was (24.50±6.81)cmH_2O.
     两组均无失败病例。 PLMA组呼吸道密封压平均为(24·50±6·81)cmH2O;
短句来源
     After the routine intravenous anesthesia induction, the PLMA and the SLMA were inserted randomly in sequence into each patient and inflated to an intracuff pressure of 60 cm H2O (1 cm H2O=0.098 kPa), airway seal pressure and lung ventilation satisfaction were evaluated, and fiberoptic (FOB) scores of the cuff anatomic position were measured.
     在常规麻醉诱导后,顺序插入PLMA和SLMA,将通气罩内压充气至60cmH2O(1cm H2O=0.098kPa),评价两种喉罩通气道充气前后的肺通气满意度和气道密封压,同时进行光导纤维支气管镜(FOB)评分,确定通气罩的解剖位置。
短句来源
     Results Without cuff inflation, airway seal pressure was higher with the PLMA than with the SLMA (P<0.05), and adequate or acceptable lung ventilation was obtained in 46 (92%) patients with the PLMA, but only 22 (44%) patients with the SLMA.
     结果在通气罩未充气情况下,插入PLMA后有46例(92%)患者获得了良好和尚可的肺通气效果,而插入SLMA后仅有22例(44%)患者获得了良好和尚可的肺通气效果; PLMA的气道密封压显著高于SLMA(P<0.05)。
短句来源
     Experiment shows that when the initial seal pressure difference of ferrofluid is bigger,the seal pressure difference reduces quickly with the increase of length to radius,while it is smaller,length to radius has less influence on seal pressure difference.
     实验结果表明:当磁性流体初始密封压差比较大时,随轴长径比的增大,密封压差迅速减小,而当初始密封压差较小时,轴长径比的增大对密封压差的影响较小;
短句来源
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  seal pressure
It is indicated that the dynamic behavior of the rotor-bearing-seal system depends on the rotation speed, seal clearance and seal pressure of the rotor-bearing-seal system.
      
Leucogranite cylinders, 3.5?mm in diameter and 7?mm in length, were run in the presence of excess H2O using cold-seal pressure vessels for 11-2,925?h.
      
Crystallization experiments were performed in cold seal pressure vessels (CSPV) and internally heated pressure vessels (IHPV) at various XH2O, under reducing (log fO2 ~ NNO) and oxidizing conditions (log fO2 ~ NNO+2.3).
      
The runs were performed in rapid-quench cold-seal pressure vessels at 0.1-0.2 GPa and 700-900?°C in the two-phase (fluid?+?melt) stability region.
      
While the secondary shoulder may seal pressure from inside or outside the pipe, that is not its function.
      
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This artical gives by theoretical analysis a general function that showspressure distribution on traditional structure of pump shaft packing seal,and indicates the two basic drawbacks which exist inevitably in the tradltionalstructure:its seal pressure distributes very unrationally, causingserious super-pressure,it can't autmatically compensate by itself afterwearing, causing troublesome in its safeguarding and more leak. To overcometwo basic drowbacks of the old structure, this artical puts forwarda...

This artical gives by theoretical analysis a general function that showspressure distribution on traditional structure of pump shaft packing seal,and indicates the two basic drawbacks which exist inevitably in the tradltionalstructure:its seal pressure distributes very unrationally, causingserious super-pressure,it can't autmatically compensate by itself afterwearing, causing troublesome in its safeguarding and more leak. To overcometwo basic drowbacks of the old structure, this artical puts forwarda new structure which is made of piston, and introduces it's first practical running test.

本文通过理论分析给出了传统结构的泵轴填料密封压紧力分布普遍式,指出了必然存在的两大基本缺点:①压紧力分布极不合理,引起严重过压;②填料磨耗后不能自动补偿,引起维护麻烦、泄漏量大。为此,提出了克服两大基本缺点的新结构──活塞压盖式填料自紧轴封,并介绍了新结构的初次应用试验情况。

Na_2SnF_6 hydrolysis reaction was investigated previously by using Morey pressure vessel (Wang et al., 1965). In the present study, the same experiments have been conducted by using the other three different pressure vessels: rapid quenching cold-seal pressure vessel (designed by Hemley J. J.), roking vessel with a golden bag (Dickson-type improved by Hemley, J. J.), and tuttle type routine cold-seal vessel at 200—647℃ and 1 kbar. The experimental results obtained are compared, suggesting that quenching...

Na_2SnF_6 hydrolysis reaction was investigated previously by using Morey pressure vessel (Wang et al., 1965). In the present study, the same experiments have been conducted by using the other three different pressure vessels: rapid quenching cold-seal pressure vessel (designed by Hemley J. J.), roking vessel with a golden bag (Dickson-type improved by Hemley, J. J.), and tuttle type routine cold-seal vessel at 200—647℃ and 1 kbar. The experimental results obtained are compared, suggesting that quenching rates would affect the precision of experimental results, especially over 400℃. The rapid quenching vessel and the rocking vessel with a golden bag are ideal apparatuses for chemical equilibrium reactions of this kind. The use of the hydrolysis method described allows one to work out the constant for hydrolysis reaction and the corresponding enthalpy.

用四种不同类型高压釜研究Na_2SnF_6在200—647℃、1 kbar条件下的水解特征。实验表明,淬火速率影响实验结果的精度。快速淬火高压釜及金袋摇摆釜是研究这类化学平衡反应的理想设备,采用水解法可获得水解常数及热焓。

In this paper , the seal capacity computation and experimental study for a high pressure differential magnetic fluid seal was carried out based on the theory of the magnetic fluid seals . The method for computing the seal pressure differential of both single-stage and multi-stage seals was presented. The seal capacity was analysed quantitatively through numerical computation on the magnetic field. It was pointed out that the seal capacity can be increased greatly by combining several multi-stage...

In this paper , the seal capacity computation and experimental study for a high pressure differential magnetic fluid seal was carried out based on the theory of the magnetic fluid seals . The method for computing the seal pressure differential of both single-stage and multi-stage seals was presented. The seal capacity was analysed quantitatively through numerical computation on the magnetic field. It was pointed out that the seal capacity can be increased greatly by combining several multi-stage seals into one seal unit, forming a multi-pole multi-stage seal. But the capacity can not be increased infinitely. Instead it tends to a limited value. Because the magnetic fluid under each stage is not equal in amount when a pressure is applied on the seal, there is a difference between the practical seal capacity and its computed value. The difference increases with the increasing of the pole number. It is believed that if the magnetic fluid can be supplemented into the sealing gap while appling the pressure differential on the seal device, the difference can be reduced and the seal capacity can be increased further. The seal pressure differential of the seal device designed in this paper reaches 1. 4MPa. The reasions for the difference between the practical and computational values of the seal capacity were discussed at the end of the paper.

本文根据磁性流体密封理论对磁性流体高压密封进行了密封能力的计算和试验研究,提出了单级与多级密封能力的计算方法,并且通过磁场的数值计算对密封能力进行了定量分析。所设计的多极-多级密封装置的密封压差可达1.4MPa。文章最后还对计算值与试验值之差异作了分析与探讨。

 
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