Mathematical model of optimum design for bevel gear transmission mechanism
In the optimization design of bevel gear transmission mechanism, the minimum volume sum of bevel gear pair is taken as […]
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Segmented hobbing of super large modified gear with standard hob
Firstly, the difference Δ n (that is, Δ n = N-N) between the minimum number of effective axial cutter teeth
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Theoretical length of hob for cutting metal in gear slot
In Figure 1, at the cutting end of the hob, although the hob teeth beyond the meshing length LM do
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Theoretical hob length for enveloping gear profile
The analysis and calculation of the cutting edge length of hob is not important for the gear with medium and
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Correction of installation angle λ of hob for super large modified gear hobbing
The practice shows that using standard hob to gear hobbing this kind of gear with incorrect method may cause abnormal
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Case analysis of gear fault based on morphological wavelet and fuzzy entropy
In order to verify the superiority of fuzzy entropy in the fault classification of transmission gears, based on the gear
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Application of fuzzy entropy in gear fault classification
Suppose that the original time series of gear fault signal is: [x (n)] = x (1), X (2) Then the
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Application of morphological wavelet in gear fault classification
Morphological wavelet is a non-linear extension of traditional linear wavelet based on mathematical morphology. Mathematical morphology and its related operators
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Stress intensity factor of helical gear root crack and influence of J-integral simulation position
Three dimensional crack models at different positions are established on the helical gear, and the stress intensity factor and J-integral
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Stress intensity factor of helical gear root crack and influence of J-integral simulation length
In order to study the effect of crack length on stress intensity factor and J-integral, the above semi elliptical initial
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Stress intensity factor of helical gear root crack and influence of J-integral simulation load
After the three-dimensional model of the gear is established, the material used in gear simulation is 17CrNiMo6, and then the
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Contact stress response characteristics of gear under fatigue pitting
As shown in the figure, the maximum contact stress response curves of the tooth surface without pitting and with pitting
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The helical gear model with initial crack is established
In order to analyze the three-dimensional crack model of helical gear root, a pair of three-dimensional helical gear models need
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Dynamic transmission error (DTE) response characteristics of gears with fatigue pitting
As shown in the figure, the DTE response curves without pitting and with pitting are drawn. Due to the periodic
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Prediction of crack stress intensity and fatigue life of helical gears
According to the measured value of stress intensity factor, kmax and Kmin can be obtained, and the range of stress
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Characteristics of pitting corrosion model of gear tooth surface
The tooth surface pitting model can be established through the gear modification parameter module in Fig. 1. By defining the
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Stress intensity factor method for helical gear crack
If the stress state of the crack and the displacement direction of the crack surface are taken as the classification
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Example analysis of contact line of cylindrical gear
In order to explain the influence of different deviation values on the contact line error and tooth profile of cylindrical
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Error analysis of contact line of cylindrical gear
In the transmission process, the contact area on the traditional gear tooth surface is a space surface, and the accuracy
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Analysis of relative position deviation between grinding wheel and cylindrical gear
In the process of cylindrical gear form grinding, the tooth surface equation of the machined cylindrical gear can be determined
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Influence of profile design of axial section of forming wheel on profile of cylindrical gear
The machining coordinate system of cylindrical gear grinding with form grinding wheel is established, as shown in Figure 1. In
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Calculation of tooth surface equation of cylindrical gear
In the process of transmission, the contact line of the line gear is formed by the motion track of the
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Types of rack and pinion pneumatic actuators for ball valves
Rack and pinion actuator is the most commonly used pneumatic actuator. The middle of the cylinder is connected with the
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Non pitting characteristic response speed of gear transmission dynamic system simulation
When the input speed frequency is 10Hz, the displacement response of master-slave gear XP is selected as the analysis object.
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Preprocessing of finite element analysis for gear shaft of feed box of C6136A lathe
From the point of view of simplification, because the gear shaft of C6136A lathe feed box is a stepped shaft,
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Dynamic model of 6-DOF gear
Based on the introduction of the corresponding mathematical model and application scenarios proposed for the dynamic physical model of gear
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Dimensional normal load and dimensional normal contact stiffness model of gear transmission system with rough tooth surface
In order to reduce the input of parameters in numerical simulation, the mathematical model of dimensional normal load is obtained
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Establishment of force model for gear shaft of feed box of C6136A lathe
Before determining the speed of the gear shaft of the feed box, the speed of the main shaft must be
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Structure of small gear and big gear ring of high temperature resistant blind valve
The loosening of the valve clamping part adopts the gear ring transmission mode. The gear ring transmission ratio is constant,
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Establishment of geometric model of wheel side meshing gear
Firstly, the 3D complex model (such as chamfering and other details) is simplified in order to reduce the difficulty of
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Force analysis of meshing gear of wheel side gear reducer
For each part of the design requirements should meet the size of the installation, power standards, long life and so
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Influence of hub deformation on meshing finite element calculation results of star gear reducer
The results of finite element analysis show that: When the rotation angle of the input end is between 0.64 rad
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Influence of hub deformation on meshing simulation model of star gear reducer
The planetary gear hub of planetary gear output type planetary gear transmission system consists of six circumferential uniformly distributed transmission
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Bifurcation characteristics of a two stage planetary gear system with varying backlash
Due to the manufacturing accuracy, installation error, lubrication requirement and space reserved for the thermal expansion of gear teeth, the
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Lyapunov exponent of nonlinear system of two stage planetary gear system
Lyapunov exponent represents the average exponential divergence rate of the distance between two adjacent trajectories in the phase plane with
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Nonlinear dynamic system excitation of two stage planetary gear system
1.Time varying meshing stiffness When the gear is in transmission, the meshing tooth pair alternates between 1 and 2, the
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Nonlinear dynamic model of two stage planetary gear system
The research object of the model is a two-stage planetary gear system, and the system diagram is shown in Figure
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Influence of tooth line radius of variable hyperbolic arc gear on meshing stiffness curve
For the variable hyperbolic arc gear, when the radius of the tooth line is small, the tooth profile surface of
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Influence of load on meshing stiffness curve of variable hyperbolic arc gear
When different loads are applied, the comprehensive elastic deformation of the tooth surface of the variable hyperbolic arc gear changes,
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Comprehensive meshing stiffness of double teeth of variable hyperbolic arc gear
After the single tooth meshing stiffness is obtained, the double tooth comprehensive meshing stiffness curve can be obtained by the
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Single tooth meshing stiffness of variable hyperbolic arc gear
The comprehensive elastic deformation UN of the pair of gear teeth is extracted by finite element post-processing, and the normal
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Iteration of modification parameters for multi-stage gear transmission system of shearer cutting section
An example is given to show the iterative process of the modification parameters. The tooth profile modification in this study
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Normal contact force and comprehensive elastic deformation of meshing tooth surface of variable hyperbolic arc gear
In order to accurately simulate the whole process of a certain tooth surface of the driving gear from entering meshing
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Simulation analysis of rough surface of gear transmission system
In order to compare and display the data intuitively, the single logarithm coordinate drawing method is used to draw the
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Establishment of finite element analysis model of variable hyperbolic arc gear
In order to calculate the stiffness of variable hyperbolic arc gear, it is necessary to calculate the normal contact force
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Contact model of asperity on rough surface of gear transmission system
According to the two-dimensional contour curve (formula) of rough surface expressed by W-M function, the morphology characteristics of rough surface
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Tooth profile modification of multistage gear transmission system of shearer cutting part
In this study, symmetrical straight line modification is used in the direction of tooth profile, and the modification curve is
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Friction mathematical model of meshing stiffness of gear transmission system
According to the actual meshing process of gear pair, the interface of a pair of gear pairs is filled with
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Digital modeling of variable hyperbolic arc gear
The principle of machining variable hyperbolic arc gear with rotating cutter head is shown in Figure 1. With double-edged cutting,
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Dynamic model of tractor planetary gear transmission system
According to Lagrange equation, the dynamic differential equation of planetary transmission system can be deduced as follows Among them, JS,
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Tooth direction repair drum of multi-stage gear transmission system of shearer cutting part
The calculation process of the modification parameter calculation method mainly includes four steps: the first step is to obtain the
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Calculation formula of meshing stiffness of variable hyperbolic arc gear
According to the forming principle of rotary cutter head, Zhao Fei et al. Verified mathematically that the middle section tooth
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Time varying meshing stiffness of tractor planetary gears
In order to ensure the continuous operation, the meshing process of gears is actually the alternating meshing of single pair
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Constraint conditions of Tractor Gear Optimization Based on mathematical analysis
According to the characteristics of objective function and planetary gear design, constraints can be divided into flexible constraints and rigid
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Dynamic simulation of multistage gear transmission system of shearer cutting part
System dynamics simulation is to obtain the actual meshing state of each gear pair. The coupling dynamic model of the
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Discrete model and boundary conditions of finite element gear pair with time-varying meshing stiffness
The basic idea of using finite element method to calculate the time-varying meshing stiffness of gear pair is to discretize
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Mathematical model of Tractor Gear Optimization
According to the large power of tractor transmission system, higher requirements are put forward for the strength and service life
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Example simulation and parameter influence analysis of meshing contact stiffness of gear tooth surface
The parameters of gear pair are selected as the calculation object, and the contact stiffness of gear pair under Yang
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Yang-sun and semi empirical contact model for meshing contact stiffness of gear tooth surface
According to the Hertz contact analysis theory, the geometric model of the contact end face of two cylinders as shown
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Formula of meshing force of single tooth considering multi-stage gear profile modification drum and support system deformation
In the following three steps, the formula of meshing force of single tooth is derived, which takes into account the