Design of automatic dynamic balancing machine for automobile generator rotor Yang Guang (School of Mechanical and Electrical Engineering, Wuhan University of Technology, Wuhan 430070, Hubei, China) The principle of linear de-coupling theory and dynamic equilibrium decoupling is discussed in detail. The research conclusions can be used for dynamic balance. Design researcher.
Due to the winding of the enameled wire and the quality of the blank, machining accuracy and the like, the rotor of the automobile generator is unbalanced after assembly.
The rotational speed of the automobile generator is getting higher and higher, and the rotor is required to be dynamically balanced. The traditional manual de-emphasis method is to repeatedly perform dynamic balance measurement on the test machine, and then perform manual drilling to remove weight, and the production efficiency and balance accuracy are low, which cannot meet the requirements of mass production. The author has participated in the development of many auto generator rotor de-balancing balancing machines, which have passed the practice test on the manufacturer's production line.
2 Overall design overview of the whole machine This equipment consists of two stations of test machine and de-weighting machine, controlled by industrial control machine (see). The rotor to be processed is tested at the test station first, and the dynamic imbalance information (the magnitude and phase of the heavy-diameter product Pr value) is automatically input to the computer, and then the rotor is placed in the de-duty station, and the computer controls the de-duty machine to the rotor. Perform de-rework to achieve dynamic balance.
Chinese display dynamic balance control electric cabinet * automatic test machine (industrial control machine) * de-heavy machine test and de-weighting two stations for the structural schematic of the automatic de-duty machine, the workpiece (rotor) is controlled by the stepper motor, it should The weight removal part is rotated to the drilling position. The rework is done by the drilling head, and the feed rate is also controlled by the stepper motor so that the bit S is exactly equal to the weight. 6. Hydraulic: The computer should de-weight the volume according to the needs of the test machine. Control the drilling depth of the de-duty machine. Since the twisted drill contact portion of the de-revolved rotor shoulder (shown) is composed of complex geometries, accurate integral calculation is very difficult. The approximation calculation method of segmentation and containment is adopted, which not only has high calculation precision, but also the calculation workload is sufficient for engineering practice.
4 claw pole shoulder optimization to redistribution In order not to affect the technical performance of the product, the quality of the car generator rotor in the claw shoulder can be de-weighted, such as a certain type of generator in each claw Only one hole of 0 mm can be drilled in the shoulder and the drilling depth should not exceed 6mn. As shown in the figure, take the left and right de-heavy planes as an example. The phase of the existing unbalanced weight-diameter product Pr is off the baseline. Discussed in two cases: a case where the drill bit is cut into a certain stage of the workpiece. The tool removal material consists of three parts: the corpse 1, the corpse 2, and the corpse. The corpse 1 and the corpse 2 are composed of a simple geometric cone and a cylinder, which can accurately calculate the volume and its centroid position. The P3 part is composed of a shoulder tapered belt, a cylindrical surface, and a plane. The integral calculation is quite complicated, but pay attention to the quality of the P3 series cutter cylinder cut-in. The mass of P3 must be greater than the mass of the truncated cone with the ABCD section as the axial section and less than the mass of the cylinder with the CDEF section as the axial section, that is, the diameter of the drill is 2r, the size of the shoulder chamfer is 2a, the height of the truncated cone is h3, and the centroid of the P3 is rotated. The radius is r3, then there is: cylinder mass P3max = å…€ factory 2 office 3 corpse round body mass p is the specific mass. The centroid of P3 takes the average of the center of mass of the cylinder and the center of mass of the circular platform: the calculated major diameter product of the drilling stage: it is obvious that the error of the calculation of the major diameter product of the above stage is completely derived from the calculation error of P3 and r3. The absolute error of the product can be estimated by the following formula: The above is only the calculation of the heavy-diameter product of the bit cutting to a certain position, and the calculation principle of drilling to other positions is the same. Through the calculation of several engineering examples, the results show that the P* claw pole de-duplication distribution schematic diagram of each bit cutting position can be de-equalized on the two claw poles according to the number of each claw pole. Let Pri and Pr2 be the heavy-diameter products of the materials removed from the two-claw poles, where Pr is the weight-diameter product of the material of the ultimate weight-removing material when the drilling depth is 6 mm.
42 Three-hole heavy-diameter product calculation If the inequality of equation (5) cannot be established, that is, the Pr value is large, and the two claw poles are de-restricted by the drilling depth limit, which cannot meet the de-weight requirement, should be considered to de-weight on the three claw poles. balance. There are countless ways to de-weight on the three claw poles. In order to maximize the efficiency of de-weighting, the minimum de-weight (drilling depth) should be considered to achieve the maximum balance, and the objective function aiming at achieving the maximum equilibrium weight-diameter product can be established: maxPr with constraints: Obviously, the above formula is a typical linear programming problem. 21, using the list simplex method, the optimal solution of the major product of the claws can be quickly obtained. The above calculation is based on the 6-claw rotor. Note that the calculation error of the median value is uniform. The claw height of the cut cTd can be fully changed when the heart is larger than the 襄. For rotors with more than 6 claw poles, the de-weighting claws are extremely more, and the (6) and (7) equations can be solved with a slight change. It can be seen that the (6) and () two formulas have general meaning.
5 Decoupling principle of dynamic balance In the engineering practice, the dynamic balance measuring end face and the de-weighting end face of the rotor are often not coincident, and the unbalanced mass of one end face will cause different inertial forces on the two measuring end faces, which is There is a decoupling problem between measurement and control de-emphasis.
As shown in the figure, it is assumed that PRi and PR2 are the major product of the unbalanced mass of the two measuring end faces, PRi and PR2 are their sizes, Pi and the heart are their phases; ri and 抒2 are two deduplications. The heavy-diameter product vector of the end face, Pri and Pr2 are their sizes, and 0i and 02 are their phases. Orders are: Among them: from the above various formulas can be derived: that is, as long as the input /, /1 / / / size, by the test of the PR PR, PR2, ..., do the equivalent value, you can calculate the deduplication end should go The size and phase of the heavy major diameter products Ph, Pb.
For the simple solution, use the trigonometric function to represent, let: 6 Conclusion This paper discusses the calculation model of the heavy-diameter product of the auto-rotor balancing machine for automobile generator rotor, and optimizes the de-weighting volume of each claw pole of the rotor. Balanced decoupling principle. The engineering practice proves that after adopting these methods, the de-balance balance precision and production efficiency of the dynamic balancing machine are improved.
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