中国机械工程学会海外会员申请指南

中国机械工程学会海外会员申请指南ＧｕｉｄｅｔｏＣＭＥＳＯｖｅｒｓｅａｓＭｅｍｂｅｒｓｈｉｐ￥ＴｈｅＣｈｉｎｅｓｅＭｅｃｈｎｌｃａｌＥｎｇｉｎｅｅｒｉｎｇＳＯＯｌｌｔｙ（ＣＭＥＳ）ｉ８８ｎａｔｉｏｎａｌｍａｓｓ０旭ａｎｌｚａｔｌｏｎｅｎｇａｇｄＩｎｓｃ...     

Guide to CMES Overseas Membership

ＧｕｉｄｅｔｏＣＭＥＳＯｖｅｒｓｅａｓＭｅｍｂｅｒｓｈｉｐＴｈｅＣｈｉｎｅｓｅＭｅｃｈｎｉｃａｌＥｎｇｉｎｅｅｒｉｎｇＳｏｃｉｅｔｙｔＣＭＥＳｊｉｓａｎａｔｉｏｎａｌｍａｓｓｏｒｇａｎｉｚａｔｉｏｎｅｎｇａｇｅｄｉｎｓｃｉｅｎｃａａｎｄｔｅｃｈｎｏｌ...     

APPROACH TO DISPATCHING FMS TOOL SYSTEM

ＡＰＰＲＯＡＣＨＴＯＤＩＳＰＡＴＣＨＩＮＧＦＭＳＴＯＯＬＳＹＳＴＥＭＬｉａｎｇＸｉｃｈａｎｇ；ＹａｎｇＹｕｅ（ＣｈｏｎｇｑｉｎｇＵｎｉｖｅｒｓｉｔｙ）Ａｂｓｔｒａｃｔ：ＤｉｓｐａｔｃｈｉｎｇｏｐｔｉｍａｌｌｙＦＭＳｔｏｏｌｓｙｓｔｅｍｃａｎｕｔｉｌｉ...     

CONTROLLED HOT FORMING OF RETAINING RING OF GENERATOR

０ＩＮＴＲＯＤＵＣＴＩＯＮＭｏｓｔｏｆｔｈｅｒｅｔａｉｎｉｎｇｒｉｎｇｓｏｆｇｅｎｅｒａｔｏｒａｒｅｃｕｒｅｎｔｌｙｍａｄｅｏｆｔｈｅｓｔｅｅｌｏｆ５０Ｍｎ１８Ｃｒ４ｏｒＭｎ１８Ｃｒ１８Ｎ．Ｉｔｂｅｃｏｍｅｓａｄｉｆｉｃｕｌｔｙｉｎｔｈｅｍａｎｕｆａ...     

WEAR TRANSITIONS OF C/Cu COMPOSITE MATERIALS

ＷＥＡＲＴＲＡＮＳＩＴＩＯＮＳＯＦＣ／ＣｕＣＯＭＰＯＳＩＴＥＭＡＴＥＲＩＡＬＳ￥ＢｕＹａｎ；ＸｉａｎｇＺｈｏｎｇｘｉａ（ＴｉａｎｊｉｎＵｎｉｖｅｒｓｉｔｙ）Ａｂｓｔｒａｃｔ：ＡｎｕｎｌｕｂｒｉｃａｔｅｄｓｌｉｄｉｎｇｆｒｉｃｔｉｏｎｔｅｓｔｏｎＣ／Ｃ...     

CHARACTERISTICS OF LOW TEMPERATURE ION PLATING TiN COATINGS

ＣＨＡＲＡＣＴＥＲＩＳＴＩＣＳＯＦＬＯＷＴＥＭＰＥＲＡＴＵＲＥＩＯＮＰＬＡＴＩＮＧＴｉＮＣＯＡＴＩＮＧＳＬｉｕＪｉｗｅｎＴｉａｎｊｉｎＵｎｉｖｅｒｓｉｔｙＹｕＬｉＩｎｓｔｉｔｕｔｅｏｆＣｏｒｏｓｉｏｎａｎｄＰｒｏｔｅｃｔｉｏｎｏｆＭｅｔａｌｓ,Ａｃ...     

ON SIMILITUDE OF CROSS-FLOW FAN IN DYNANIC PERFORMANCE AND NOISE CHARACTER

ＯＮＳＩＭＩＬＩＴＵＤＥＯＦＣＲＯＳＳ－ＦＬＯＷＦＡＮＩＮＤＹＮＡＮＩＣＰＥＲＦＯＲＭＡＮＣＥＡＮＤＮＯＩＳＥＣＨＡＲＡＣＴＥＲＣｈｅｎＣｉｃｈａｎｇＪｉａｎｇｓｕＵｎｉｖｅｒｓｉｔｙｏｆＳｃｉｅｎｃｅａｎｄＴｅｃｈｎｏｌｏｇｙＡｂｓｔｒａｃｔＴｈｅ...     

SYNTHESIS OF GUIDED CHAIN DRIVE MECHANISM WITH LINKAGE

ＳＹＮＴＨＥＳＩＳＯＦＧＵＩＤＥＤＣＨＡＩＮＤＲＩＶＥＭＥＣＨＡＮＩＳＭＷＩＴＨＬＩＮＫＡＧＥＳｈａｎＢａｏｚｈｏｎｇＷｕＫｅｙｏｎｇＣｈａｎｇｃｈｕｎＩｎｓｔｉｔｕｔｅｏｆＯｐｔｉｃｓａｎｄＦｉｎｅＭｅｃｈａｎｉｃｓＷａｎｇＹｉｘｉｎｇＣｈｅｎＥｎ...     

COORDINATE MEASURING MACHINE PROBING ACCESSIBILITY

0　ＩＮＴＲＯＤＵＣＴＩＯＮＣｏｏｒｄｉｎａｔｅｍｅａｓｕｒｉｎｇｍａｃｈｉｎｅ (ＣＭＭ )ｉｓｔｈｅｋｅｙｄｅｖｉｃｅｕｓｅｄｉｎｃｏｍｐｕｔｅｒ ｉｎｔｅｇｒａｔｅｄｄｉｍｅｎｓｉｏｎａｌｉｎｓｐｅｃｔｉｏｎ .Ｈｏｗｅｖｅｒ,ｆｒｏｍｔｈｅ ｐｅｒｓｅｃｔｉｖｅｏｆｆｕｎｃｔｉｏｎａｌｉｔｙ ,ｉｔｉｓｍｅｒｅｌｙａｎａｃｃｕｒａｔｅｄｉｇｉｔｉｚｅｒ ,ｒｅｑｕｉｒｉｎｇｌｅｎｇｔｈｙ ｐｌａｎｎｉｎｇ ,ｆｏｒｉｎｓｐｅｃｔｉｎｇｃｏｍｐｌｅｘｗｏｒｋｐｉｅｃｅｓ.Ｉｎ ａｎｉｎｓｐｅｃｔｉｏｎ ｐｌａ…     

A MODIFIED HEAT CONDUCTION MODEL

ＡＭＯＤＩＦＩＥＤＨＥＡＴＣＯＮＤＵＣＴＩＯＮＭＯＤＥＬＡＭＯＤＩＦＩＥＤＨＥＡＴＣＯＮＤＵＣＴＩＯＮＭＯＤＥＬＨａｒｒｙＧｉｎｇｏｌｄ；ＤｉｎｅｓｈＧｅｒａ（ＤｅｐａｒｔｍｅｎｔｏｆＭａｔｈｅｍａｔｉｃｓ）（ＤｅｐａｒｔｍｅｎｔｏｆＭｅｃｈａｎｉｃ...     

评定三坐标测量机的动态误差

对三坐标测量机的动态误差作出整体分析。分析影响坐标测量机动态误差的主要因素。指出由于附加惯性力的影响产生的各部件绕气浮导轨联结处的偏转和各运动部件本身的弯曲变形是造成动态误差的主要原因。提出由动态偏转角误差推导测头动态位移误差的方法。用激光干涉仪和电感测微仪对三坐标测量机的动态偏转角误差进行了测量。理论和实验结果证明,在高速测量过程中,由于附加惯性力的影响,除了各部件绕气浮导轨联结处产生较大偏转外     

三坐标测量机动态误差的建模方法

为了提高三坐标测量机的测量速度,缩短测量周期,分析了影响给定的三坐标测量机动态误差的因素。对三坐标测量机的具体和了分析,用电感测微仪进行了动态偏转角的测量,并推导出由动态偏转误差得到测头处的动态位移误差的方法。同时,对由导轨的直线度造成的误差进行了讨论。指出动态误差主要是由各构件绕气浮导轨连接处的偏转和各运动构件本身的弯曲变形造成挫理论上可以证明,在气浮导轨力矩刚度和横梁弯曲刚度已知的情况下,只要     

Multibody contact dynamics on mechanisms with deep groove ball bearing joints

The dynamics of ball bearings are important to fatigue breakage, dynamic performance and motion precision of mechanisms connected by ball bearings joints with multi-clearances. In this study, a new method is proposed for multibody dynamics analysis on mechanisms under the effects of radial internal clearances and impact of balls/cage pockets interactions of ball bearings. Including balls/rings interactions and balls/cage pockets interactions, the three dimensional dynamics models of the crank slider mechanism are established and calculated by generalized-α algorithms on the basis of Hertzian contact theory and penalty function method. The rules of eccentric trajectories of inner and outer ring center for one ball bearing joint are verified with the results calculated by XU’s references. The results of dynamic errors, motion trajectories, dynamic forces are achieved under different speeds, radial clearances and number of ball bearings. The speeds and radial clearances are critical to the dynamic performances and motion precision of mechanisms, especially the number of ball bearings. The number of ball bearings is important to impact force and motion stability of the mechanism.     

Linear motion carriage with aerostatic bearings preloaded by inclined iron core linear electric motor

A fundamentally precise and simple linear motion axis design is discussed where the attractive force from the linear motor is used to preload a carriage supported by six rigidly attached porous carbon air bearings. The air bearings are assembled by vacuuming the pads to two orthogonal planes, positioning the carriage above the pads, and then injecting epoxy between the bearings and the carriage. Control of flatness tolerances of the bearings and planes permits over-constraint of the carriage by the bearings, which leads to a high degree of accuracy and moment load capacity via elastic averaging. Good dynamic stiffness is also obtained because of large bearing area and squeezed-film damping. The two orthogonal planes represent an accurate and cost effective geometry that can be created to guide linear motion; and by placing the open-face iron-core motor at the desired position and angle with respect to the bearings, preload forces with equal or otherwise desired relative magnitudes are obtained. Because the attractive force is typically 3–5 times the axial force generated by the motor, the system is inherently stable even in the presence of large externally applied moments that might otherwise induce excessive pitch, yaw, or roll errors.     

Dynamics of universal joints, its failures and some propositions for practically improving its performance and life expectancy

A universal joint also known as universal coupling, U joint, Cardan joint, Hardy-Spicer joint, or Hooke??s joint is a joint or coupling in a rigid rod that allows the rod to ??bend?? in any direction, and is commonly used in shafts that transmit rotary motion. It consists of a pair of hinges located close together, oriented at 90° to each other, connected by a cross shaft. The Cardan joint suffers from one major problem: even when the input drive shaft rotates at a constant speed, the output drive shaft rotates at a variable speed, thus causing vibration and wear. The variation in the speed of the driven shaft depends on the configuration of the joint. Such configuration can be specified by three variables. The universal (Cardan) joints are associated with power transmission systems. They are commonly used when there needs to be angular deviations in the rotating shafts. It is the purpose of this research to study the dynamics of the universal joints and to propose some practical methods for improving their performance. The task is performed by initially deriving the motion equations associated to the universal joints. That is followed by elaborating on the oscillatory behavior in the rotational speed and the torque that transmits through the intermediary shaft. The forces in the joint bearings are calculated by using an analytical method that is also supported by the numerical modeling. Such models are also used in order to calculate the rhythm and the amount of the excess loads on the joint. This is suggested as a systematic procedure in the search for the causes of the failures in these popular bearings. With the same purpose in mind some defected bearings with deformed sections were selected for the laboratory examinations. By analyzing the loading behavior and the surface conditions of the defected bearings and by comparison with the known fatigue theories attempts are made in order to dig into the causes for the failures in these joints and their bearing surfaces. With the aim of improving the performance and the life expectancy of these popular elements of the machineries, some practical recommendations are also suggested.     

A musculoskeletal lumbar and thoracic model for calculation of joint kinetics in the spine

The objective of this study was to develop a musculoskeletal spine model that allows relative movements in the thoracic spine for calculation of intra-discal forces in the lumbar and thoracic spine. The thoracic part of the spine model was composed of vertebrae and ribs connected with mechanical joints similar to anatomical joints. Three different muscle groups around the thoracic spine were inserted, along with eight muscle groups around the lumbar spine in the original model from AnyBody. The model was tested using joint kinematics data obtained from two normal subjects during spine flexion and extension, axial rotation and lateral bending motions beginning from a standing posture. Intra-discal forces between spine segments were calculated in a musculoskeletal simulation. The force at the L4-L5 joint was chosen to validate the model’s prediction against the lumbar model in the original AnyBody model, which was previously validated against clinical data.

     

MEMS-based rotary strapdown inertial navigation system

As the inertial navigation completely depends on the sensed acceleration and rotation rate by IMU, the sensor errors accumulate and eventually lead to diverged inertial solutions. Therefore the compensation of the inertial sensor errors is an effective approach to improve the SINS navigation performance. The rotation error modulation in rotary SINS, which has been extensively used for the filter-optical IMU in the past, is one of the techniques to compensate or mitigate the inertial sensor errors and eventually improve the system navigation performance. The rotary SINS is an inertial navigator in which the IMU is installed on the rotational platform and rotated following the pre-designed rotation configuration, and the rotation error modulation is the technique that compensates the navigation errors caused by inertial sensor bias in a complete rotation cycle by rotating IMU. Given the auto-compensation of inertial sensor bias in rotation error modulation, the objective of this paper to develop a MEMS-based rotary SINS, in which the significant sensor bias is automatically compensated by rotating the IMU, to offer the comparable navigation performance to tactical-grade IMU. Simulation results indicate that, compared with the conventional method, the proposed approach attenuates the navigation errors and improve the calibration accuracy based on the reciprocating rotation scheme can be used to automatically improve the observability.     

Dynamic force coefficients and the mechanism of instability in hydrostatic journal bearings

In experiments with hydrostatic bearings it has been found that a whirl instability occurs as the rotational speed is increased to a critical value. The onset frequency is predicted in this paper and the mechanism of the whirl is discussed. It is shown that the dynamic forces at the onset of whirl may be represented by a simple vector diagram. Analytical expressions are presented which allow the dynamic forces to be calculated. The derived dynamic coefficients may be applied to bearings with any number of recesses, and also to non-whirling bearings. Experiments have shown good correlation with predicted onset conditions.     

Rotor System Oscillations under the Rotor Rotation Inside Floating Elements

Rotor system oscillations are considered for the rotation of the rotor inside lightweight moving elements (for example, inside floating seal rings, and hydrostatic bearings). In this case, the ring runs around the rotor in a direct precession mode (hula-hoop type of oscillations). The oscillations of the rotor-floating ring system are studied taking into account hydrodynamic forces in the gap and contact forces of dry friction. A solution is obtained in analytical form. It is shown that the ring precession speed under the running-around is close to its own frequency at a given rotation speed. Trajectories are plotted for the motion of the ring.     

Fluid Flow Analysis for Friction Torque around Rolling Element in Ball Bearings

Ball bearings (e.g., deep-groove, angular-contact, and roller bearings) support loads in a rotor system and provide lubrication between the shaft and housing. The deep-groove ball bearings used in a turbopump do not differ significantly from angular-contact ball bearings or the bearings found in other applications. Deep-groove ball bearings consist of rolling elements, an inner raceway, an outer raceway, and a retainer to guide the rolling elements. In ball bearings, the resistive (churning or drag) forces and torques acting on the rolling elements and raceways are affected by the fluid flow rate and direction, as well as the rotational speed. These churning and drag forces and torques affect the internal dissipation or power losses into the bearing, which become very significant for high-speed applications. This study numerically investigated the characteristics of the flow conditions for deep-groove ball bearings, with a particular focus on the friction distribution on the rolling elements. A simple analytical model of the fluid flow inside a ball bearing was developed using a computational analysis, and the flow characteristics at high rotational speeds are presented.