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.

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.

To introduce structure and process design of horizontal adjustable predeformation apparatus according to production require of FNR series multilayer stands non rotation ropes.

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

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.

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.

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.

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

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.

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.

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.