70 results about "Pressure angle" patented technology

The invention discloses a cam curve pressure angle optimization method of a continuous zooming infrared lens. The method comprises the following steps: S1, obtaining cam curve digital coordinate data of a to-be-optimized part; s2, pressure angle distribution characteristics are obtained; s3, selecting an optimization strategy according to the pressure angle distribution characteristics; s4, performing global piecewise function angle redistribution on the cam curve to be optimized; and S5, processing constraint inspection, motion constraint inspection, smoothness constraint inspection and pressure angle constraint inspection are performed according to the constraint conditions, and an optimized result is output after target requirements are met. According to the method, the cam curve can be accurately detected, and various parameters of the curve can be effectively optimized.

The invention discloses a method for increasing the sidewall turn-up height in a building process of an all-steel radial tire, which comprises the following steps of: acquiring multi-source data such as temperature, pressure and angle in a turn-up process through an infrared temperature sensor, a pressure sensor and the like; and constructing a multiple linear regression model, a machine learning model and a hybrid model fused with the physical principle, analyzing the relationship between the process parameters and the anti-package height, and performing verification and optimization. According to model output parameters, a servo motor is used for accurately controlling the downward pressing angle and pressure of a reverse wrapping pressing roller, and production is executed in cooperation with an auxiliary supporting ring and a sectional type reverse wrapping technology; meanwhile, the turn-up height is detected in real time through an intelligent monitoring system, and parameters are automatically adjusted when the turn-up height does not reach the standard. According to the method, precise regulation and control of the tire sidewall turn-up height are achieved, compared with a traditional process, the product percent of pass is increased to 95% or above from 85%, the production efficiency is improved by 20%-30%, the tire structure stability is effectively enhanced, the rolling resistance and the tire burst risk are reduced, and intelligent upgrading of tire manufacturing is promoted.

The invention provides a design method of a full-life diamond roller for a powerful inner honing wheel. The design method comprises the steps that design parameters of the diamond roller are determined according to parameters of an outer gear and the inner honing wheel; the design parameters of the diamond roller comprise a normal modulus Mn, a circle dividing normal pressure angle Afn, a helix angle Bf2, a tooth number Z2, a displacement coefficient Xn2, an addendum circle diameter Deg2, a root circle diameter Dig2 and an effective starting circle diameter dyx2; and calculating the addendum circle diameter and addendum width of the diamond roller. According to the parameters of the new inner honing wheel and the old inner honing wheel, design parameters of the two sets of diamond rollers are determined respectively, and then the design parameters of the full-life diamond roller are obtained through intersection; the tooth crest width of the diamond roller is checked, it is guaranteed that the tooth crest does not become sharp, parameters of the diamond roller are optimized, the optimality of the honing process is guaranteed, the diamond roller is designed only in 20 minutes at present, and compared with dozens of hours in the prior art, efficiency is greatly improved, and the new product development period is shortened.

The invention discloses a spline meshing characteristic calculation method based on a time-varying meshing position. The spline meshing characteristic calculation method comprises the following steps: establishing a spline meshing state characterization model of a spline; the spline tooth backlash and the pressure angle containing parallel misalignment of the spline are obtained through the spline meshing state characterization model; establishing a spline single-tooth meshing stiffness calculation model through a potential energy method, the spline tooth backlash and the pressure angle; spline tooth meshing deformation coordination conditions are obtained according to the spline single-tooth meshing rigidity calculation model; a spline meshing deformation calculation method of the spline is obtained according to the spline tooth meshing deformation coordination condition; establishing a spline meshing force model containing parallel misalignment according to a spline meshing deformation calculation method; and acquiring spline meshing characteristics of the spline according to the spline meshing force model. According to the method, a spline meshing force model containing parallel misalignment is established; the spline meshing characteristics can be described more accurately, and the design of a high-speed, high-reliability and low-vibration mechanical transmission system is facilitated.

The application provides a design and calculation method of main parameters of helical gear flowmeter, and belongs to the technical field of flowmeter. The design and calculation method is obtained by theoretically analyzing the helical gear flowmeter, and the influence of the number of gears, modulus, pressure angle, helix angle, radial clearance of the flowmeter and end face clearance of the flowmeter on the flow pulsation, clearance flow leakage and power loss of the helical gear flowmeter is discussed. In combination with the particle swarm optimization algorithm, two of the three performance indexes, flow pulsation, leakage and power loss, are changed into constraint conditions according to the design requirements, so that the multi-objective problem is changed into a single-objective problem for solving the main parameters of the helical gear flowmeter. Compared with the traditional method of calculating the displacement of the flowmeter through the empirical formula and the empirical coefficient, the application can improve the displacement design precision of the flowmeter, can clearly determine the influence degree of each parameter on the performance of the flowmeter, and can quickly solve the main parameters of the helical gear flowmeter through the optimization algorithm.

The utility model provides a kind of gap elimination gear assembly, gear transmission system and robot, gap elimination gear assembly includes: first gear;Second gear, with first gear coaxial arrangement, can rotate relative to first gear, and can be moved relative to first gear along the axial direction of first gear, the number of teeth of second gear and first gear, modulus and pressure angle are all same;At least one first guide portion, it is set to the end surface of first gear close to second gear along the circumference of first gear;At least one second guide portion, it is set to the end surface of second gear close to first gear along the circumference of second gear;Second gear moves relative to first gear along the axial direction of first gear, and second guide portion and first guide portion are along the circumference of first gear sliding fit, and rotate relative to first gear.The utility model's gap elimination gear assembly can realize no side gap gear transmission, effectively reduce the dead stroke error of gear transmission, still can keep stable gap elimination state in bidirectional transmission.

The utility model discloses a kind of seat pitch adjusting device, including logging truck, the cab of logging truck is equipped with seat, and seat is installed in cab by bottom plate, the lower end of seat is equipped with buffer unit, and the lower end of buffer unit is equipped with top plate, adjusting mechanism is equipped between bottom plate and top plate, for adjusting seat pitch angle;The utility model is equipped with horizontal inclination sensor by setting the adjusting range of adjusting mechanism ±15 °, can read the inclination angle of logging truck, then control motor rotation adjusts and compensates the inclination angle of seat;While using circular arc guide rail slider as main structure, structure gap is small firm stable;Using the adjusting mode of cam groove and cam slider combination, motor and screw rod are used as power to push cam slider, while the cam structure with large pressure angle has self-locking ability, so that the adjusting mechanism has greater carrying capacity, while it can meet the demand of frequent adjustment.

The present disclosure relates to a gearbox housing, comprising an input-side housing, a side housing and an output-side housing, wherein the input-side housing and the output-side housing are connected to the side housing by means of a plurality of bolt holes arranged along the side housing; the input-side housing is provided with first and second bearing seats and a plurality of radial rib plates; the plurality of radial rib plates include first radial rib plates and second radial rib plates; each first radial rib plate extends radially outward from the center of the first bearing seat, and each second radial rib plate extends radially outward from the center of the second bearing seat; the radial rib plates are connected to the bolt holes; the direction connecting the center of the first bearing seat and the center of the second bearing seat is a first direction, and a second direction is perpendicular to the first direction; around the center of the first bearing seat, in the areas deviating ±30° of a pressure angle relative to the second direction, the first radial rib plates and the bolt holes are arranged more densely than in other areas, the pressure angle being the pressure angle of the pressure acting on the first bearing seat. The gearbox housing of the present disclosure can achieve beneficial effects such as inhibiting deformation, improving supporting stiffness and facilitating heat dissipation.

The invention relates to a membrane disc flexible coupling, and relates to the field of couplings. According to the technical scheme, an inner and outer tooth meshing pair with matched modulus and pressure angle is additionally arranged on the membrane disc and the protective plate, so that an efficient emergency torque transmission structure is constructed; when the coupler works normally, meshing interference of inner teeth and outer teeth can be effectively avoided by means of the reserved transmission gap, and it is ensured that the flexible compensation performance of the membrane disc is not affected; once the membrane disc is damaged, the inner teeth and the outer teeth can be quickly meshed to form a temporary torque transmission path. Under the condition, the operation limitation of a traditional coupler is broken through, torque can be continuously transmitted after the diaphragm disc loses efficacy, precious emergency shutdown or maintenance time is won for equipment such as a large compressor and a generator set, production interruption and safety accidents caused by sudden shutdown of the generator set are fundamentally avoided, and the operation reliability of related equipment is remarkably improved.

The application discloses a kind of heavy load AGV wheel edge reduction unit asymmetric high coincidence planetary gear train optimization design method, it is related to artificial intelligence automatic driving field, including: the power, rotational speed and temperature parameter of wheel edge reduction unit operation are collected, dimensionless standardization processing is carried out based on benchmark working condition value, determines the working condition fluctuation interval corresponding to each parameter;Uniform sampling is carried out through the working condition fluctuation interval determined in step one, obtain several groups of working condition sample data, with the minimum gear face contact stress and root bending stress as optimization goal, solve the gear optimal design parameter corresponding to each group of working condition sample data;The application establishes the quantitative mapping relationship of working condition fluctuation and gear design parameter, so that modulus, pressure angle, tooth width and the like parameter can adapt to the change of load, rotational speed, temperature, improve the problem that optimal parameter is difficult to determine in traditional design relying on artificial experience iteration.

The invention provides a differential gear mechanism and a design method thereof. In the differential gear mechanism of the present disclosure, a reference pressure angle of each side gear tooth of a side gear and a reference pressure angle of each pinion tooth of a pinion gear increase from an intermediate portion of a tooth trace toward an inner end side and from the intermediate portion toward an outer end side, and the reference pressure angle of each side gear tooth of the side gear and the reference pressure angle of each pinion tooth of the pinion gear increase from the intermediate portion toward the outer end side. The tooth thickness of the pitch cone of the side gear decreases from the intermediate portion of the tooth trace toward the inner end side and increases from the intermediate portion toward the outer end side. The tooth thickness of the pitch cone of the pinion gear increases from the intermediate portion of the tooth trace toward the inner end side and decreases from the intermediate portion toward the outer end side.

The application discloses a gear design optimization method based on a Bayesian algorithm, and relates to the technical field of gear design. A tooth surface geometric model is established based on the pure rolling relationship of a rack and a gear, a load stiffness coupling model is constructed by combining meshing partition and a tooth direction slicing method, contact and bending stress are obtained, and drive and non-drive side pressure angles, addendum height coefficients, dedendum fillet radius coefficients, radial variables and tooth widths are taken as design parameters. A multi-objective function of minimizing maximum dedendum bending stress, maximum contact stress and maximizing average overlapping degree is set. A Markov blanket structure is introduced to screen key variables, a Gaussian process is used to establish a proxy model, and an improved acquisition function based on an expected hypervolume is used for iterative optimization. The number of iterations, the improvement amplitude and the running time limit are taken as termination conditions. The optimal parameters are screened by combining a normalized comprehensive score. The gear design optimization method based on the Bayesian algorithm can improve the design accuracy of asymmetric high-overlapping gears and the efficiency of design parameter optimization.

The utility model discloses a transfer gear bevel gear set structure of a gearbox of a 5-ton loader. The transfer gear bevel gear set structure comprises transfer gears, a variable-speed pump shaft gear and a steering pump shaft gear. The transfer gear, the variable-speed pump shaft gear and the steering pump shaft gear are all of a helical tooth structure, the tooth number of the transfer gear is Z53, the tooth number of the variable-speed pump shaft gear is Z53, the tooth number of the steering pump shaft gear is Z63, the pressure angle is 20 degrees, and the helical angle is 15 degrees. The distance between the transfer teeth and the shaft gear of the variable-speed pump is 183 + / -0.03 mm, and the distance between the transfer teeth and the shaft gear of the steering pump is 203 + / -0.03 mm, so that a transfer tooth bevel gear set structure is installed on an original box body, and the transmission precision is ensured. The transfer gear set is stable in transmission, low in vibration and noise and high in bearing capacity, and solves the problems of high vibration and noise and weak bearing capacity during transmission of the transfer gear set in the prior art.

The invention discloses a method for calculating the cross-ball distance of asymmetric inner and outer back taper teeth. The method comprises the following steps of: 1, solving basic parameters of a workpiece, wherein the basic parameters comprise a base circle diameter, an original circle division end surface pressure angle and actual circle division helical angles on the left and right sides of an inclined back taper; 2, deducing the cross-ball distance at the position L of any cross section of the tooth pitch large end of the outer inclined back taper: solving the tooth thickness of the original large end face of the outer inclined back taper, the arc tooth thickness of the end face of any T cross section, the equivalent original normal arc tooth thickness of the T cross section, the equivalent original circle dividing normal displacement coefficient, the involute angle of the equivalent ball measuring center circle pressure angle of the T cross section and the ball measuring center circle pressure angle; and finally, calculating the cross-ball distance of the cross section of the odd and even teeth of the outer inclined inverted conical teeth at any distance L from the large end. According to the method, a solution is given, a calculation formula of the solution is deduced and the technical problem is solved by aiming at the difficulty of the cross-ball distance of the inner and outer inclined inverted conical teeth of the large gear ring, a theoretical calculation method of the cross-ball distance of the inverted conical teeth is perfected through three-dimensional modeling verification that the error is extremely small, and the method has guiding significance on field processing and detection of the inclined inverted conical teeth.

The invention discloses a special tooth root digging and gear shaping method. The method comprises the following steps of firstly calculating involute meshing starting circles dnf1 and dnf2 of two gears by utilizing the tooth number Z, modulus m, pressure angle alpha and mounting center distance a of paired meshing gears; calculating the tooth space width K at the starting circle dnf of the gear according to a standard calculation formula; and after the value of K is determined, a single tooth root shaping method is adopted, the width of the slotting tool is equal to the tooth groove width K, the slotting tool is aligned with the tooth groove center of the standard reserved grinding gear to shape the tooth root, and the tool can be stopped when the tooth root circle diameter df is equal to (Z-2. 5) m. A special tooth root digging gear shaping method is adopted to replace a special reserved grinding root digging hob, and the problems that the special reserved grinding root digging hob is narrow in adaptability, high in price and high in cost are solved.

The present application provides a drive gear of a fishing reel. The drive gear (11) has a circular plate portion (30) and a plurality of gear teeth (31). The circular plate portion (30) has a rotational axis (X). The plurality of gear teeth (31) respectively protrude from a side surface on an outer peripheral side of the circular plate portion (30) in a direction extending toward the rotational axis (X). The gear teeth (31) have a main body portion (32) and an extension portion (33). A first angle (a11, a12) formed by a cylindrical surface (CP1) passing through a tooth top surface (31c) of the main body portion (32) and a radially inner side surface (31d) of the extension portion (33) is larger than an engagement pressure angle (b). Accordingly, the present application provides a drive gear of a fishing reel capable of improving a rotation feeling.

The invention discloses a full-automatic blowout preventer turnover device and a control method, and relates to the technical field of blowout preventer turnover control, and the device comprises a base, a turnover beam, a turnover base, a hydraulic cylinder group, an arc-shaped supporting plate, a pulley vehicle, a hydraulic locking pin and a control system. The base is arranged below the overturning base, the overturning beam is rotationally connected with the overturning base, the arc-shaped supporting plate abuts against the blowout preventer, the hydraulic locking pin limits relative rotation of the overturning beam and the overturning base, and the control system is electrically connected with all execution components. According to the control method, overturning of the blowout preventer is achieved through mode switching, staged linkage overturning and automatic control of the locking pin, an overturning load threshold value is dynamically calculated through the weight sensor and the pressure sensor, the gravity center of the blowout preventer is inversely calculated in combination with pressure-angle data in the initial overturning stage so as to calibrate parameters, and the overload protection and state monitoring functions are achieved. The automatic degree, safety and adaptability of blowout preventer overturning operation are improved, and the blowout preventer overturning device is suitable for blowout preventer overhauling in the field of petroleum drilling.

This utility model relates to the field of seismic testing equipment technology, and in particular to a testing device for the seismic performance of building structures. It includes a housing and a rebound hammer body. The housing is fixedly connected to the outer surface of the rebound hammer body. An adjustment mechanism is provided inside the housing. The adjustment mechanism includes a U-shaped plate, an adjustment cylinder, a buffer cylinder, a buffer plate, and a connecting rod. A U-shaped groove is formed on the side wall of the housing. The U-shaped plate is slidably connected to the inner side wall of the U-shaped groove. This utility model, through the cooperation of the U-shaped plate, housing, and suction cup, utilizes the adjustment cylinder and suction cup to apply pressure to the rebound hammer. First, the sealing plate is squeezed to firmly fix the suction cup to the U-shaped plate. Then, the housing and rebound hammer can only move perpendicularly towards the wall along the U-shaped plate, ensuring the accuracy of the pressure angle and avoiding errors caused by angle deviation, thus maintaining the accuracy of the test results.

This utility model discloses a plug compression testing device, relating to the technical field of testing devices, including a mounting plate and a compression assembly; the mounting plate has four corresponding legs fixed to its lower side, and a base plate fixed to the lower end of the four legs. A clamping assembly is installed in the middle of the mounting plate, and a fixing assembly and a rotating assembly are installed on the upper side of the clamping assembly. The left side of the rotating assembly is connected to the fixing assembly; the compression assembly includes a fixing strip, a first hydraulic rod, a connecting strip, a connecting plate, and a pressure sensor. A fixing hole is provided on the upper side of the mounting plate, and a fixing strip is fixed inside the fixing hole. Two corresponding first hydraulic rods are installed on the lower side of the fixing strip. A connecting strip is fixed on the telescopic arm of the first hydraulic rod, and a connecting plate is fixed between the two connecting strips. A groove is provided in the middle of the connecting plate, which can quickly adjust the pressure angle of the plug according to the requirements.

The application provides a plastic worm gear tooth thickness optimization design method, device, equipment and storage medium, and the method comprises the following steps: calculating geometric parameters according to the number of teeth, modulus, pressure angle and input torque of worm gear transmission; a first functional relationship between worm gear shearing stress and tooth thickness displacement coefficient is established; a second functional relationship between worm gear root bending stress and tooth thickness displacement coefficient is established through root dangerous section analysis; the optimal tooth thickness displacement coefficient is solved and the best tooth thickness is obtained by taking the minimum worm gear shearing stress as the target and the worm gear root bending stress not exceeding the allowable stress as the constraint. The plastic worm gear shearing stress model and the metal worm gear root bending stress model are established, and both are included in the unified optimization framework, the optimal design of the worm gear tooth thickness is realized under the premise of ensuring the strength of the worm gear, the limitation that the prior art only focuses on the strength of a single part is overcome, the blindness of the experience design is avoided, and the design efficiency and quality are improved.

The present application relates to a kind of heavy load industrial robot and gap adjustment calculation method.The gap adjustment calculation method of a kind of heavy load industrial robot described in the present application includes the following steps:S1: provide heavy load industrial robot;S2: obtain the meshing angle and pressure angle of input bevel gear;S3: calculate the normal force generated at the tooth surface width midpoint on the pitch cone surface of input bevel gear;S4: according to meshing angle, pressure angle and normal force, calculate the axial force generated on the tooth surface of input bevel gear;S5: calculate the first compression length of compression spring;S6: according to axial force and first compression length, select the compression spring with appropriate elastic coefficient k and original length, so that the first elastic force generated by compression spring is greater than or equal to the axial force of shaft tooth.The five-sixth axis structure and gap adjustment calculation method of a kind of heavy load industrial robot described in the present application have the advantages of simple debugging, convenient maintenance and high running stability.

The invention relates to the technical field of harmonic speed reducers, and provides a high-stability gear speed reducer with a good heat dissipation effect, the high-stability gear speed reducer comprises an input shaft, an output shaft, a first cycloidal gear, a second cycloidal gear and a gear ring, and the output shaft, the first cycloidal gear, the second cycloidal gear and the gear ring are sequentially arranged in the axial direction of the axis of the input shaft; the first cycloidal gear and the second cycloidal gear are both meshed with the inner gear, the gear is an involute gear with short tooth height and large pressure angle, and synchronous reverse input of power is achieved through the arrangement of the first eccentric wheel, the second eccentric wheel and other structures and the arrangement of the input shaft, the first eccentric wheel and the second eccentric wheel which are oppositely arranged in the reverse direction. According to the technical scheme, rotary motion is converted into reciprocating motion of the cycloidal gear by combining the second transmission bearing and the third transmission bearing, efficient speed reduction transmission is achieved through meshing of the small-tooth-difference inner gear and the cycloidal gear, the single-stage transmission ratio is large, the structure is flattened, and the problems that in the prior art, speed reduction transmission efficiency is low and stability is insufficient are solved through the technical scheme.

The utility model relates to the technical field of automobile speed reducers, in particular to a coaxial electric driving system which comprises a motor assembly. The motor assembly is connected with a planet row type speed reducing mechanism; the planet row type speed reducing mechanism is connected with a cylindrical gear differential mechanism; the cylindrical gear differential mechanism is connected with wheels; the planet row type speed reducing mechanism and the cylindrical gear differential mechanism are coaxially arranged; gears in the cylindrical gear differential mechanism adopt the same design of common gear parameters such as tooth number, meshing radius, width and gear pressure angle; the internal structure of the speed reducer can be compact, and the overall structure can be lightened.

The invention belongs to the technical field of friction plates, and particularly discloses a method and a system for acquiring bending-twisting-shaft-swinging coupling random collision dynamic characteristics of a floating support friction plate, and the method comprises the following steps: acquiring basic parameters of the floating support friction plate and an inner hub, constructing a three-dimensional tooth surface profile of the floating support friction plate and the inner hub in an ideal state, and obtaining a three-dimensional tooth surface tooth profile, a contact position pressure angle and a separation distance in a random irregular motion state; and calculating the comprehensive rigidity of the floating support friction plate at the meshing position and the nonlinear normal collision force at the meshing position of the floating support friction plate and the inner hub gear teeth, constructing a bending-twisting-shaft-swinging coupling vibration random collision dynamic model of the inner hub and the floating support friction plate, and determining the dynamic characteristics of the inner hub and the floating support friction plate at each moment. By the adoption of the technical scheme, the influence of the coupling effect between meshing deviation excitation and rigidity excitation of the inner hub and the friction plate gear teeth is considered, high calculation efficiency is guaranteed, and a more accurate dynamic response rule is obtained.

A gear unit is proposed comprising a cylindrical worm (2, 22, 202) driven to rotation about a geometric worm axis (3, 23, 203), and a cross-worm gear (5, 35, 45, 55, 65, 105, 205) which has a helical toothing (7, 37) on one face (6, 36). The worm (2, 22, 202) meshes with at least one thread in the toothing of the cross-worm gear (5, 35, 45, 55, 65, 105, 205) and thereby drives the cross-worm gear (5, 35, 45, 55, 65, 105, 205) to rotation about a geometric cross-worm gear axis (8, 68, 108, 208). The geometric worm axis (3, 23, 203) and the geometric worm gear axis (8, 68, 108, 208) are skew geometric straight lines relative to each other. Each tooth of the helical gearing (7) of the worm gear (5, 35, 45, 55, 65, 105, 205) has a convex tooth flank (10) and a concave tooth flank (11).The thread (4) of the worm (2, 22, 202) has an asymmetrical profile with a first thread flank (4a, 204a) and a second thread flank (4b, 204b). The first pressure angle α between the convex tooth flank (10) and the first thread flank (4a, 204a) is smaller than the second pressure angle α between the concave tooth flank (11) and the second thread flank (4b, 204b).

The application discloses a kind of robust optimization design method of double pressure angle asymmetric gear modification parameters considering uncertain working condition, steps include: defining the torque value range of gear service condition uncertainty and geometric design requirement;Gear pair meshing performance simulation model is constructed and simulation test design is carried out;Establish the multi-objective optimization model of modification parameter with the target of comprehensive service performance index and comprehensive robustness index;Pareto solution set is obtained by using intelligent optimization algorithm;Select the best scheme and export gear three-dimensional model.The application will load spectrum fluctuation into asymmetric gear modification optimization, through the combination of proxy model and multi-objective optimization, realize the gear modification parameter design with strong robustness to uncertain working condition, significantly improve the transmission stability and reliability of gear under variable load condition, while greatly reduce the calculation cost and time in optimization design process.

This invention relates to an industrial robot and a method for calculating clearance adjustment. The method for calculating clearance adjustment of an industrial robot according to this invention includes the following steps: S1: providing an industrial robot; S2: obtaining the meshing angle γ, helix angle β, and pressure angle α of an input hyperboloid gear; S3: calculating the circumferential force F1 along the tangential direction on the tooth surface of the input hyperboloid gear; S4: calculating the axial force F generated on the bevel gear surface based on the meshing angle γ, helix angle β, pressure angle α, and circumferential force F1. a S5: Calculate the first compression length L1 of the compression spring; S6: Based on the axial force F a A compression spring with a suitable elastic coefficient k and an original length L0 is selected for the first compression length L1, so that the compression spring generates a first elastic force F. 弹1 Axial force F greater than or equal to the shaft tooth a The five- or six-axis module structure of an industrial robot and the calculation method for gap adjustment described in this invention have the advantages of simple debugging, convenient maintenance, and high operational stability.

The utility model discloses a motor five -axis rotary table with dustproof function, including bottom plate, the bottom plate top fixed mounting has rocking arm subassembly, rocking arm subassembly includes: two bearing seat, dustproof shield, fixed frame, dust screen, first motor, first helical gear, second helical gear and rotary table subassembly, by the dustproof shield, replaceable dust screen etc. Composed multilevel dustproof system is constructed, has guaranteed heat dissipation ventilation while effectively blocking dust invasion core transmission area, has improved the adaptability and durability of rotary table under the severe working condition significantly, it adopts helical gear meshing transmission (beta1 equals -beta2) and keeps gear pair modulus and pressure angle consistent, has guaranteed the high stability of transmission, low noise and long -term precision, in addition the design of replaceable dust screen makes routine maintenance very convenient, has reduced life cycle cost greatly.

The utility model relates to a deburring device which comprises a connecting assembly and a spline idler wheel, the connecting assembly is used for connecting the spline idler wheel to a lathe tool turret, and the spline idler wheel is configured to rotate around the axis of the spline idler wheel. A spline of the spline roller and a spline of a to-be-deburred part have the same modulus, and the spline tooth number of the spline roller and the spline tooth number of the part are relatively prime; the spline pressure angle of the spline roller is different from the spline pressure angle of the part; and a spline of the spline roller is provided with a helical angle. Through the arrangement of the spline roller, when the part spline needs to be deburred, the spline roller is close to the groove part of the part, the spline of the spline roller is meshed with the part spline, and along with rotation of the part, the spline of the spline roller and the part spline extrude each other, so that the burrs on the part spline can be flattened; and the deburring treatment on the spline of the part is realized. Meanwhile, manpower is saved, the probability of errors is smaller, and therefore damage to parts is reduced.

The invention provides a design method of a curve groove of a zoom cam lever and a zoom mechanism, and the method comprises the steps: obtaining data columns of the moving distances of a zoom lens group and a compensation lens group through optical software simulation, arranging the data columns, determining data and data serial numbers of a circle of rotation of the zoom cam lever, and calculating the curve groove of the zoom cam lever; and by adjusting the radius of the zoom cam lever or calculating the rotation angle of the corresponding point, it is ensured that all the pressure angles in the data column are not larger than the allowable pressure angle. According to the width of the curve groove and the minimum wall thickness of the curve groove, the minimum moving distance of one circle of curve winding is limited, so that the inner wall of the curve groove is smooth in the whole process and not prone to deformation, it is guaranteed that excellent imaging quality is obtained, smooth movement of the zoom guide pin can be guaranteed, a zoom mechanism is not prone to being blocked or even stuck, jumping of an optical axis is reduced, and the service life of the zoom mechanism is prolonged. And the driving torque of the motor for driving the zoom cam rod to rotate is reduced.