Corrector alignment method and device

Abstract

The invention discloses a corrector alignment method and device, and aims to solve the problems that errors are superposed, adjustment depends on experience and the efficiency is low when a correction roller is assembled. The device takes a main shaft as a benchmark, an eccentric fine tuning assembly is arranged to realize radial quantitative fine tuning, an axial compensation assembly compensates end face runout by means of end face height difference, and stability is guaranteed by matching with an axial fixing assembly and a dynamic balance assembly. According to the method, the radial run-out and the end face run-out of the roller are accurately controlled and corrected to be smaller than or equal to 0.002 mm through four steps of operation including reference assembly, radial quantitative fine adjustment, axial cooperative compensation and fixed balance. The device does not need to be disassembled repeatedly, improves the aligning efficiency, reduces vibration, is suitable for different sizes and rotating speed scenes, and is suitable for precise grinding equipment.

Description

Technical Field

[0001] This invention relates to the field of machining technology, specifically to a method and apparatus for calibrating a corrector, which is suitable for precision grinding scenarios where high accuracy of grinding wheel profile calibration is required. Background Technology

[0002] In the precision grinding process, the dressing roller is a key component customized according to the workpiece. Its installation accuracy directly determines the calibration quality of the grinding wheel profile, thus affecting the final machining accuracy of the workpiece. According to industry precision grinding technical standards, the end face runout and radial runout of the dressing roller during installation must be strictly controlled within 0.002mm. This accuracy index is a core prerequisite for ensuring the profile accuracy after grinding wheel dressing and avoiding excessive workpiece machining errors.

[0003] From the perspective of actual production and assembly processes, although the correction roller is manufactured according to the same precision standards and can meet the runout accuracy requirements when tested individually, when it is assembled into the machine tool roller drive spindle (i.e., spindle 1 in this technical solution), it is often difficult to consistently achieve the runout accuracy requirement of 0.002mm due to the superposition of errors from multiple links. These errors mainly come from three key links: First, the precision fit clearance between the spindle and the inner hole of the correction roller. Even with transition fit or clearance fit, a small fit clearance will still cause radial or axial positional deviations. Second, the form and position tolerances inherent in the machine tool spindle system (such as radial runout and end face runout of the spindle) will be directly transmitted to the correction roller, causing additional errors. Third, the positioning deviation and uneven force of the operator during assembly, such as the coaxiality calibration deviation between the correction roller and the spindle, and the end face tilting caused by uneven tightening torque of the fixing screws, further aggravate the accuracy deviation.

[0004] Currently, the industry's solutions to the aforementioned accuracy issues mainly rely on the traditional "trial and error adjustment method": operators need to repeatedly disassemble the correction roller, use measuring tools such as dial indicators to check the runout value, and iteratively optimize it by adding or removing shims, rotating and adjusting the installation angle, etc., until the runout accuracy meets the standard. This traditional adjustment method has obvious technical limitations: on the one hand, the repeated disassembly, measurement, and adjustment process is time-consuming and labor-intensive, with a single adjustment often taking 30-60 minutes, seriously consuming equipment time and reducing production efficiency; on the other hand, the adjustment effect is highly dependent on the operator's experience and skill level, and the accuracy consistency is poor under different operators and different adjustment scenarios, making it difficult to guarantee the long-term stability of the correction roller installation accuracy, which in turn leads to fluctuations in the grinding wheel correction quality and affects the reliability of batch workpiece processing accuracy.

[0005] Furthermore, while existing self-aligning mechanisms for correction rollers (such as simple self-aligning structures based on eccentric worm gears) can achieve a certain degree of radial or axial fine-tuning, they generally suffer from the defects of "separation of adjustment dimensions" and "lack of quantitative reference": the adjustment of radial runout and axial runout must be operated independently, lacking a coordinated compensation mechanism, which easily leads to the contradiction of "damaging axial accuracy when adjusting radial accuracy"; at the same time, there is no clear scale indication or quantitative calculation method during the adjustment process, making it impossible to accurately control the fine-tuning amount, resulting in over-adjustment or under-adjustment, further prolonging the operation time, and still failing to fundamentally solve the problems of accuracy control efficiency and stability.

[0006] In summary, existing assembly and adjustment technologies for correction rollers have room for improvement in terms of accuracy stability, adjustment efficiency, and ease of operation. There is an urgent need for a self-aligning solution that can achieve coordinated radial and axial adjustment, has a quantitative benchmark, and is highly efficient in operation, in order to solve the problem of achieving accuracy standards due to the superposition of errors during assembly. Summary of the Invention

[0007] The purpose of this invention is to overcome the shortcomings of existing technology in the self-alignment of correction rollers, which are characterized by "lack of quantization, difficulty in coordination, and low efficiency". It provides a method and device for corrector alignment, and achieves rapid and accurate self-alignment of correction rollers through an integrated solution of "radial fine-tuning quantization + axial runout coordination compensation + dynamic balance optimization".

[0008] This corrector calibration method includes the following steps: 1) Base assembly: Fit the graduated ring onto the small diameter section of the spindle, ensuring a clearance fit between the inner hole of the graduated ring and the small diameter section; fit the eccentric worm gear onto the small diameter section, with the lower end face of the worm gear against the upper end face of the graduated ring; fit the correction roller with the worm gear through its inner hole, ensuring the lower end face of the correction roller abuts against the upper end face of the worm gear; fix the U-shaped bracket to the plane of the spindle, and mesh the worm on the U-shaped bracket with the worm gear, with the worm axis parallel to the spindle axis; 2) Eccentric fine-tuning radial: Connect an external drive tool to the non-circular torsion drive part of the worm gear, rotate the worm gear to drive the worm wheel to rotate around the small diameter section; read the rotation angle of the worm wheel and quantify the radial fine-tuning amount by means of the reference line on the spindle and the angle scale on the outer circumference of the scale ring; monitor and correct the radial runout of the roller in real time until the runout value is ≤0.002mm, and lock the radial position by means of the self-locking characteristics of the worm gear and the worm wheel; 3) Axial compensation: Measure the runout value of the correction roller end face, rotate the scale ring, and use the height difference between the upper and lower end faces of the scale ring to make the high point of the scale ring face in the opposite direction of the axial deviation, and compensate the end face runout to ≤0.002mm. 4) Fixing and balancing: Cover the upper end face of the correction roller with the pressure plate, so that the shank of the large screw passes through the through hole of the pressure plate and is threaded into the screw hole of the small diameter section. Tighten the large screw to fix the worm gear, correction roller and scale ring axially. Install a counterweight on the second plane of the spindle, and the weight of the counterweight is equal to the total weight of the U-shaped frame and the worm to balance the radial imbalance.

[0009] The present invention also provides a corrector alignment device, comprising: Spindle: The upper end is coaxially narrowed to form a small diameter section, and a screw hole coaxial with the small diameter section is opened at the center of the upper end face of the small diameter section; Plane 1 and Plane 2 are parallel to each other on the outer peripheral wall of the spindle near the small diameter section, and Plane 1 and Plane 2 are symmetrical about the spindle axis; A reference line parallel to the spindle axis is etched on the outer peripheral wall of the spindle near the scale ring. Eccentric fine-tuning assembly: includes a U-shaped frame, a worm gear, and an eccentric worm wheel; the U-shaped frame is fixed to a plane by screws, and two opposing upright plates of the U-shaped frame have coaxial rotating holes, the axis of which is parallel to the axis of the main shaft; both ends of the worm gear pass through the rotating holes and form a rotating fit, the lower end of the worm gear has a non-circular torsion drive part, and the outer peripheral wall of the worm gear has an annular groove corresponding to the outer side of the U-shaped frame upright plate, and an open-type annular retaining spring is installed in the annular groove, the outer diameter of which is larger than the diameter of the rotating hole; the inner hole of the worm wheel is transitionally fitted with the small diameter section, the eccentricity between the axis of the inner hole of the worm wheel and the outer circular axis is 0.005-0.02mm, the worm wheel meshes with the upper end of the worm gear, and the middle part of the worm wheel extends upward along the axis to form an integrally formed sleeve, the inner cavity of the sleeve is concentric with the inner hole of the worm wheel and has the same diameter; Axial compensation component: a graduated ring, fitted onto the small diameter section and located below the worm gear, with a clearance fit between the inner hole of the graduated ring and the small diameter section; the upper and lower end faces of the graduated ring are not parallel, with a difference of ≤0.003mm between the high and low points; the outer circumferential wall of the graduated ring is uniformly etched with angle graduations along the circumference, with an angle graduation accuracy of 0.1°, used to align with the baseline to quantify the rotation angle of the worm gear; Axial fixing assembly: includes pressure plate and large screw; the pressure plate has a through hole in the middle that is adapted to the shank of the large screw, and the lower surface of the pressure plate is used to abut against the upper end face of the correction roller; after the shank of the large screw passes through the through hole of the pressure plate, it is threaded into the screw hole of the small diameter section. Dynamic balancing component: a counterweight block, fixed to plane two by screws. The weight of the counterweight block is equal to the total weight of the U-shaped frame and the worm gear, and the counterweight block and the U-shaped frame are symmetrical about the main axis. Connection components: The correction roller is evenly provided with multiple axial countersunk through holes along the circumference; the worm gear is provided with multiple axial small threaded holes corresponding to the axial countersunk through holes; it also includes multiple small screws, the shank of which passes through the axial countersunk through holes and is threadedly connected to the axial small threaded holes one by one, and the head of the small screw is recessed into the axial countersunk through holes.

[0010] The beneficial technical effects of the present invention are as follows: 1. Quantitative collaborative alignment improves both accuracy and efficiency simultaneously. By coordinating the angle scale of the graduated ring with the spindle baseline, precise control of the radial fine-tuning amount of the correction roller can be achieved, eliminating the reliance on operational experience. At the same time, the graduated ring has both "axial compensation" and "radial fine-tuning quantification indication" functions, solving the problem of the separation between traditional radial and axial adjustments, greatly shortening the single self-alignment time, and significantly improving self-alignment efficiency.

[0011] 2. Structural synergy optimization enhances overall operational stability. The sleeve of the eccentric worm gear and the inner hole of the correction roller form radial auxiliary positioning, improving the coaxiality performance of the correction roller and the main shaft; the counterweight and the U-shaped frame are symmetrically distributed about the main shaft axis and have matching weights, effectively suppressing the vibration when the main shaft rotates, avoiding the vibration from interfering with the self-aligning accuracy, and ensuring the long-term stable operation of the device.

[0012] 3. Extremely simple operation design, greatly improving ease of maintenance. The worm gear achieves axial positioning through a ring snap ring, eliminating the need for additional limiting structures and simplifying the assembly process. Axial fixing can be completed simply by tightening the large screw. Subsequent maintenance and replacement of the correction rollers significantly reduce the number of operation steps, lowering the complexity of use and maintenance. Attached Figure Description

[0013] Figure 1 This is a schematic diagram of the structure of the device of the present invention.

[0014] Figure 2 for Figure 1 A magnified view of a portion of the image.

[0015] Figure 3 for Figure 1 A sectional view.

[0016] Figure 4 for Figure 1 Partial diagram.

[0017] Figure 5 for Figure 1 Another perspective on the component separation.

[0018] Reference numerals: 1 - main spindle, 11 - minor diameter section, 12 - screw hole, 13 - baseline, 14 - plane two, 2 - U-shaped bracket, 21 - rotating hole, 3 - worm gear, 31 - torsion drive, 32 - annular groove, 4 - worm wheel, 41 - sleeve, 42 - small screw hole, 5 - large screw, 6 - pressure plate, 7 - small screw, 8 - annular retaining ring, 9 - graduated ring, 10 - counterweight, 100 - correction roller, 101 - countersunk through hole. Detailed Implementation

[0019] In the description of this invention, it should be noted that the terms "upper," "lower," "left," and "right" indicate orientations or positional relationships based on the written form. These orientations or positional relationships are only for the convenience of describing this invention and simplifying the description, and do not indicate or imply that the device or element referred to must have a specific orientation, or be constructed and operated in a specific orientation, and therefore should not be construed as limiting the invention.

[0020] In the description of this invention, it should be noted that, unless otherwise explicitly specified and limited, the terms "installed," "connected," and "connected" should be interpreted broadly. For example, they can refer to a fixed connection, a detachable connection, or an integral connection; they can refer to a mechanical connection or an electrical connection; they can refer to a direct connection or an indirect connection through an intermediate medium; and they can refer to the internal connection of two components. Those skilled in the art can understand the specific meaning of the above terms in this invention based on the specific circumstances.

[0021] The following specific embodiments illustrate the implementation of the present invention. Those skilled in the art can easily understand other advantages and effects of the present invention from the content disclosed in this specification. Obviously, the described embodiments are only some, not all, of the embodiments of the present invention. Based on the embodiments of the present invention, all other embodiments obtained by those skilled in the art without creative effort are within the scope of protection of the present invention.

[0022] Example 1: The alignment device and operation of the φ50mm correction tool are described in reference to... Figure 1-5 .

[0023] This embodiment is applicable to the φ50mm diamond dressing roller 100, which is suitable for the grinding wheel dressing process of a precision cylindrical grinding machine. It requires that the radial runout and end face runout after installation do not exceed 0.002mm.

[0024] 1. Device component parameters and principle description (1) Main spindle 1 40Cr material is selected, which is high in strength and easy to machine. The upper end of the main shaft 1 is coaxially reduced to form a small diameter section 11, with a diameter of φ15mm and a length of 30mm. This small diameter section 11 serves as the mounting reference shaft for the correction roller 100, and its cylindricity error is controlled within 0.0005mm to ensure reference accuracy. A screw hole 12 with an M8×1.25 specification is opened at the center of the upper end face of the small diameter section 11 for axial fixation using a large screw 5.

[0025] Two planes, 13 and 14, are located on the outer peripheral wall of the main spindle 1 near the minor diameter section 11. Both planes are 10 mm wide and 2 mm deep, and are symmetrical about the axis of the main spindle 1, with a symmetry error controlled within 0.01 mm. This provides a structural foundation for the subsequent installation of the dynamic balancing components. A 0.2 mm wide red reference line 13 is etched on the outer peripheral wall of the main spindle 1 near the scale ring 9. The reference line 13 is parallel to the axis of the main spindle 1 and serves as a visual reference for angle quantification, facilitating alignment with the angle scale of the scale ring 9.

[0026] (2) Eccentric fine-tuning component Core principle: The worm gear 3 drives the eccentric worm wheel 4 to rotate. By utilizing the axial offset (i.e., eccentricity) between the inner hole and the outer circle of the worm wheel 4, the rotational motion of the worm wheel 4 is converted into the radial fine-tuning motion of the correction roller 100, thereby achieving radial runout precision control.

[0027] U-shaped frame 2: Made of aluminum alloy, it features a lightweight design to reduce radial weight imbalance. The U-shaped frame 2 is fixed to plane 13 with screws. The distance between its two opposing uprights is 20mm. A rotating hole 21 with a diameter of φ8mm is provided on each upright. The axis of the rotating hole 21 is parallel to the axis of the main shaft 1, with a parallelism error not exceeding 0.01mm, ensuring precise meshing between the worm gear 3 and the worm wheel 4.

[0028] Worm 3: Module 1, Number of threads 1, Lead angle 3°. The lead angle of 3° is less than the equivalent friction angle (approximately 5°) of the meshing tooth surfaces of worm 3 and worm wheel 4, satisfying the self-locking condition, and can maintain the adjusted position without the need for an additional locking structure. The lower end of worm 3 is provided with a torsion drive part 31, which has a regular hexagonal groove structure with a side-to-side distance of 6mm, and is compatible with a standard Allen wrench for applying torque.

[0029] An annular groove 32 is formed on the outer peripheral wall of the worm gear 3, corresponding to the outer side of the U-shaped frame 2 vertical plate. The annular groove 32 is 2mm wide and 0.5mm deep. An annular retaining spring 8 is installed in the annular groove 32. The annular retaining spring 8 is a shaft open retaining ring with a specification of φ8mm and an outer diameter of φ12mm, which is larger than the diameter of the rotating hole 21. It can effectively limit the axial displacement of the worm gear 3 and prevent the meshing clearance from increasing due to axial movement.

[0030] Worm gear 4: Module 1, number of teeth 40. The meshing transmission ratio between worm 3 and worm gear 4 is 1:40, meaning that for every one revolution of worm 3, worm gear 4 rotates 9°, allowing for fine adjustment. The inner diameter of worm gear 4 is φ15mm, forming a transition fit with the small diameter section 11. The fit clearance is controlled between 0.001 and 0.003mm, ensuring both the flexibility of worm gear 4's rotation and limiting its radial runout.

[0031] The eccentricity between the inner bore axis and the outer circular axis of the worm gear 4 is 0.01 mm, which falls within the range of 0.005~0.02 mm specified in the claims. Too small an eccentricity will result in insufficient adjustment range, while too large an eccentricity will make precise control difficult. A sleeve 41 extends axially upwards from the middle of the worm gear 4. The sleeve 41 and the worm gear 4 are integrally formed. The sleeve 41 has a diameter of φ20 mm and a length of 15 mm. The inner cavity of the sleeve 41 is concentric with the inner bore of the worm gear 4 and has the same diameter. The inner bore of the correction roller 100 forms a clearance fit with the outer peripheral wall of the sleeve 41, with a clearance of 0.002~0.005 mm. This clearance provides radial auxiliary positioning for the correction roller 100, reducing its radial wobble.

[0032] (3) Axial compensation assembly Core principle: Utilizing the non-parallel characteristics (i.e. height difference) between the upper and lower surfaces of the scale ring 9, the contact position between the scale ring 9 and the worm gear 4 is changed by rotating the scale ring 9, thereby compensating for and correcting the end face runout of the roller 100, similar to the height compensation principle of "inclined shims".

[0033] Scale ring 9: Made of 45 steel, hardened to improve hardness and wear resistance. The outer diameter of scale ring 9 is φ30mm and the inner diameter is φ15.01mm. It forms a clearance fit with the small diameter section 11 with a clearance of 0.01mm to ensure the rotational flexibility of scale ring 9.

[0034] The upper and lower surfaces of the scale ring 9 are not parallel, and the difference between their high and low points is 0.002mm. This value does not exceed 0.003mm, which meets the requirements for end face runout compensation. The outer circumferential wall of the scale ring 9 is uniformly etched with angle graduations along the circumference, with a graduation range of -90° to +90° and an angle accuracy of 0.1°. The 0° graduation corresponds to the high point of the end face, and the ±90° graduations correspond to the low point of the end face. Combined with the baseline 13, the rotation angle can be quantified to achieve precise control of the compensation amount.

[0035] (4) Axial fixing assembly Pressure plate 6: Made of 65Mn material, which has good elasticity and can prevent excessive deformation during clamping. Pressure plate 6 has a diameter of φ45mm and a through hole with a diameter of φ8.5mm in the middle, which is compatible with the shank of large screw 5.

[0036] Large screw 5: An M8×25 socket head cap screw is selected. The shank of large screw 5 passes through the through hole of pressure plate 6 and is threaded into the threaded hole 12 of small diameter section 11. Tightening large screw 5 drives pressure plate 6 to apply downward pressure along the spindle 1, axially pressing the worm gear 4, correction roller 100, and graduated ring 9, eliminating gaps between components and preventing runout during rotation. Tests have verified that when the tightening torque of large screw 5 is controlled at 5 N·m, it ensures the tightening effect without causing component deformation.

[0037] (5) Dynamic balancing components Core principle: The total mass of the counterweight 10, the U-shaped frame 2, and the worm gear 3 is equal, and the two are symmetrical about the axis of the main shaft 1. This can counteract the centrifugal couple generated when the main shaft 1 rotates, reduce vibration, and ensure operational stability.

[0038] Counterweight 10: Made of brass, weighing 80g, equal to the total weight of U-shaped frame 2 and worm gear 3. Counterweight 10 is fixed to plane 14 with M4 screws. After installation, the symmetry error between counterweight 10 and U-shaped frame 2 about the axis of spindle 1 does not exceed 0.02mm, effectively balancing the radial imbalance generated by U-shaped frame 2 and worm gear 3.

[0039] (6) Connecting components The correction roller 100 has four countersunk holes 101 evenly spaced circumferentially, each with a diameter of φ4.5mm. The worm gear 4 has four small threaded holes 42 corresponding to the countersunk holes 101, each with an M4 specification. The small screws 7 are M4×10 socket head cap screws. The shanks of the small screws 7 pass through the countersunk holes 101 of the correction roller 100 and are threaded into the corresponding small threaded holes 42 of the worm gear 4.

[0040] The small screws 7 are evenly spaced circumferentially (the included angle between two adjacent small screws 7 is 90°), which ensures the coaxiality of the dressing roller 100 and the worm gear 4, with the coaxiality error controlled within 0.002mm. At the same time, the heads of the small screws 7 are recessed into the countersunk through holes 101 and will not protrude from the surface of the dressing roller 100, thus avoiding interference with the grinding wheel dressing operation.

[0041] 2. Assembly and self-aligning operation steps (1) Reference assembly Assemble in the following order to ensure accurate initial positioning of each component, laying the foundation for subsequent alignment: 1. Insert the scale ring 9 into the small diameter section 11 of the spindle 1, and initially adjust the position of the scale ring 9 so that the 0° scale line of the scale ring 9 is aligned with the reference line 13 of the spindle 1; 2. Fit the worm gear 4 into the small diameter section 11, ensuring that the lower end face of the worm gear 4 is in close contact with the upper end face of the scale ring 9. The roughness of the contact surface is controlled within Ra0.8μm to reduce the impact of contact deformation on accuracy. 3. Place the correction roller 100 on the outer peripheral wall of the sleeve 41 of the worm gear 4, and pass three small screws 7 through the countersunk through holes 101 of the correction roller 100 and screw them into the corresponding small screw holes 42 of the worm gear 4. Tighten the small screws 7 to a torque of 2 N·m to avoid excessive torque causing deformation of the worm gear 4. 4. Fix the U-shaped bracket 2 onto plane 13 of the spindle 1 with M3 screws. During installation, adjust the position of the U-shaped bracket 2 to ensure that the worm 3 and worm wheel 4 are precisely meshed. The meshing clearance should be controlled between 0.01 and 0.02 mm. If the clearance is too large, it will cause reverse backlash; if it is too small, it may cause jamming. 5. Fix the counterweight 10 to the plane 14 with M4 screws. After installation, use a dial indicator to measure the deviation of the counterweight 10 and the U-shaped frame 2 from the axis of the main shaft 1 to ensure that the two are symmetrical about the axis of the main shaft 1, and the symmetry error does not exceed 0.02mm.

[0042] (2) Radial runout quantization fine-tuning 1. Measure the initial deviation: Fix the dial indicator on the grinding machine worktable, so that the dial indicator probe is perpendicular to the outer cylindrical surface of the correction roller 100. After starting the dial indicator and zeroing it, manually and slowly rotate the spindle 1. The initial radial runout of the correction roller 100 is measured to be 0.004mm. This deviation mainly comes from the fit clearance between the spindle 1 and the correction roller 100 and the eccentricity during the assembly process. 2. Application of fine-tuning principle: According to the radial fine-tuning calculation method defined by the claim, the fine-tuning amount = eccentricity of worm wheel 4 × sinθ (θ is the rotation angle of worm wheel 4). By rotating worm 3 to drive worm wheel 4 to rotate, the rotational motion of worm wheel 4 is converted into the radial displacement of correction roller 100. 3. Precise Adjustment Operation: Select an Allen wrench compatible with the torsion drive unit 31 of the worm gear 3, insert it into the torsion drive unit 31, and slowly rotate the worm gear 3. During the rotation, closely observe the alignment of the reference line 13 of the spindle 1 with the outer circumference of the scale ring 9. When the reference line 13 is aligned with the 10° scale line of the scale ring 9, stop rotating the worm gear 3. At this time, the rotation angle θ of the worm wheel 4 is 10°. Substituting the eccentricity of 0.01mm, the fine adjustment amount is 0.01×sin10°≈0.0017mm. 4. Accuracy verification: Manually rotate the spindle 1 again. The dial indicator shows that the radial runout of the correction roller 100 has dropped to 0.0015mm, which meets the accuracy requirement of ≤0.002mm. The current position is maintained by utilizing the self-locking characteristics of the worm gear 3 and worm wheel 4, without the need for additional locking.

[0043] (3) Axial runout coordinated compensation 1. Measure the initial deviation: Adjust the position of the dial indicator so that the dial indicator probe is perpendicular to the upper end face of the correction roller 100. Manually and slowly rotate the spindle 1. The initial end face runout of the correction roller 100 is measured to be 0.003mm. This deviation mainly comes from the non-parallelism of the end face of the scale ring 9 and the tilting during the assembly process. 2. Application of the compensation principle: By rotating the scale ring 9, the height difference between its upper and lower end faces is used to change the support height of the worm gear 4, thereby compensating for the end face runout of the correction roller 100. For example, if the initial end face is in a "left high, right low" state, the high point of the scale ring 9 can be turned to the right, raising the height of the right side to offset the deviation of the left side being too high; 3. Precise compensation operation: Hold the outer circumference of the scale ring 9 with your hand and slowly rotate it to align the +30° scale line of the scale ring 9 with the reference line 13 of the main shaft 1. At this time, the right side of the scale ring 9 is higher than the left side. Based on the height difference of 0.002mm of the scale ring 9, the compensation amount is approximately 0.002×sin30°=0.001mm. 4. Accuracy verification: Manually rotate spindle 1 again. The dial indicator shows that the end face runout of the correction roller 100 has dropped to 0.001mm, which meets the accuracy requirement of ≤0.002mm, and the axial compensation is completed.

[0044] (4) Verification of axial fixation and dynamic balance 1. Axial fixing operation: Cover the upper end face of the pressure plate 6 with the correction roller 100, align the through hole in the middle of the pressure plate 6 with the screw hole 12 of the small diameter section 11 of the main shaft 1, pass the shank of the large screw 5 through the through hole of the pressure plate 6 and thread it into the screw hole 12, tighten the large screw 5 to a torque of 5 N·m with a torque wrench, and axially press the worm gear 4, correction roller 100 and scale ring 9 through the pressure plate 6 to eliminate the gap between the components and fix the adjusted position; 2. Dynamic balance verification: Start the spindle 1 to the rated speed of the grinding machine 3000 r / min, and use a vibration meter to detect the vibration amplitude of the spindle 1 during operation. The measured amplitude is 0.0008 mm. The vibration amplitude is small, indicating that the counterweight 10 effectively balances the radial imbalance generated by the U-shaped frame 2 and the worm gear 3. The overall accuracy and stability of the device meet the requirements of precision grinding.

[0045] Example 2: Alignment device and operation for φ100mm correction device This embodiment is applicable to a φ100mm cubic boron nitride dressing roller 100, which is adapted to a precision surface grinder. It requires that the radial runout after installation does not exceed 0.002mm and the end face runout does not exceed 0.0015mm, further verifying the versatility of the technical solution of the present invention.

[0046] 1. Optimization of device component parameters (1) Main spindle 1 The diameter of the minor section 11 is increased to φ20mm and the length to 35mm to accommodate the installation requirements of the large-diameter correction roller 100; the screw hole 12 at the center of the upper end face of the minor section 11 is changed to M10×1.5 to improve the axial fixing strength; the width of plane 13 and plane 2 14 is increased to 15mm and the depth is increased to 3mm to provide installation space for the larger U-shaped frame 2 and counterweight 10.

[0047] (2) Eccentric fine-tuning component The worm gear module 3 is changed to 1.25, the number of threads remains 1, and the lead angle is changed to 2.5° (still meeting the self-locking condition). The torsion drive part 31 is changed to a square head structure with a side-to-side distance of 8mm, which is suitable for wrenches with larger torque. The module of worm gear 4 is changed to 1.25 and the number of teeth is changed to 36. The meshing transmission ratio between worm 3 and worm gear 4 is changed to 1:30 (worm rotates 1 revolution, worm gear rotates 12°), the adjustment speed is faster, and it can meet the deviation compensation requirements of large diameter rollers. The eccentricity between the inner hole and the outer circle of worm gear 4 is increased to 0.02mm (within the range of 0.005~0.02mm as defined in the claims), which increases the radial adjustment range. The width of the annular groove 32 is increased to 2.5mm and the depth is increased to 0.6mm. The annular retaining ring 8 is changed to a shaft retaining ring with a specification of φ10mm and an outer diameter increased to φ16mm to adapt to the size change of the worm gear 3.

[0048] (3) Axial compensation assembly The outer diameter of the scale ring 9 is increased to φ50mm and the inner diameter is increased to φ20.01mm, maintaining a clearance fit with the small diameter section 11; the height difference between the upper and lower end faces of the scale ring 9 is increased to 0.003mm (compliant with the ≤0.003mm limit in the claims), improving the end face runout compensation capability; the scale range remains -90° to +90° with an accuracy of 0.1°, ensuring the accuracy of angle quantification.

[0049] (4) Dynamic balancing components The weight of counterweight 10 is increased to 120g, which is equal to the total weight of the larger U-shaped frame 2 and worm gear 3. It also adopts a symmetrical double counterweight design (two counterweights are symmetrically distributed along plane 14) to further reduce vibration during high-speed rotation.

[0050] (5) Connecting components The correction roller 100 has six countersunk holes 101 evenly spaced around its circumference, and the worm gear 4 has six small screw holes 42 of M5 specification at the corresponding positions. The small screws 7 are replaced with M5×12 internal hex countersunk screws. The six small screws 7 are evenly spaced around the circumference (adjacent included angle 60°) to improve the connection stability between the large diameter correction roller 100 and the worm gear 4 and ensure coaxiality.

[0051] 2. Key operational differences (1) Radial fine adjustment Because the eccentricity of the worm gear 4 increases to 0.02mm, when the reference line 13 is aligned with the 15° scale line of the scale ring 9, the rotation angle of the worm gear 4 is θ=15°, and the fine adjustment amount is 0.02×sin15°≈0.005mm, which can offset the large initial radial deviation of the large diameter correction roller 100 (the initial runout is usually 0.005~0.006mm), and the final radial runout can be reduced to 0.0018mm, which meets the accuracy requirements.

[0052] (2) Axial compensation The large-diameter correction roller 100 is prone to slight end-face tilt due to its own weight, with an initial end-face runout typically of 0.004~0.005mm. During adjustment, align the -45° scale line of the scale ring 9 with the reference line 13. At this point, the compensation amount = 0.003 × sin45° ≈ 0.0021mm, which can reduce the end-face runout to 0.0014mm, meeting the accuracy requirement of ≤0.0015mm.

[0053] (3) Axial fixation The large-diameter correction roller 100 requires greater axial clamping force, and the tightening torque of the large screw 5 is increased to 8 N·m to ensure that all components fit tightly and avoid intermittent jumping during rotation.

[0054] Example 3: Device Optimization for Scenarios with High Vibration Suppression Requirements This embodiment focuses on high-speed grinding machines (spindle speed 1 6000 r / min), emphasizing enhanced dynamic balance performance and vibration suppression capabilities, and verifying the effectiveness of the dynamic balance components and structural optimization scheme in the claims.

[0055] 1. Optimized design of the device (1) Optimization of dynamic balancing components The counterweight 10 is made of tungsten alloy, which has a density of 19.3 g / cm³, 2.3 times that of brass. This allows for a 40% reduction in volume for the same weight, reducing rotational inertia and minimizing centrifugal force fluctuations during high-speed rotation. The weight of the counterweight 10 remains equal to the total weight of the U-shaped frame 2 and worm gear 3, and precision tooling ensures a symmetry error of ≤0.01 mm with the U-shaped frame 2, further enhancing the balance.

[0056] (2) Optimization of eccentric fine-tuning components Molybdenum disulfide solid lubricant is applied to the meshing tooth surfaces of the worm 3 and worm wheel 4. Molybdenum disulfide has a friction coefficient of only 0.05, which can significantly reduce frictional vibration during meshing transmission (frictional vibration is one of the main vibration sources during high-speed rotation), while improving the wear resistance of the meshing surfaces and extending service life.

[0057] (3) Optimization of axial compensation components The clearance between the inner hole of the scale ring 9 and the small diameter section 11 is reduced to 0.005mm, which reduces the radial movement of the scale ring 9 during high-speed rotation (the movement will cause additional vibration). At the same time, a small amount of lubricating oil is applied to the mating surface of the scale ring 9 and the small diameter section 11 to reduce the rotational friction resistance.

[0058] 2. Effect Verification (1) Vibration suppression effect When the spindle 1 is running at a speed of 6000 r / min, the amplitude measured by a high-precision vibration meter is 0.0005 mm, which is 40% lower than that in Example 1. This indicates that the balancing effect of the tungsten alloy counterweight 10 and the friction-reducing effect of the molybdenum disulfide lubricant are significant, meeting the low vibration requirements of the high-speed grinding machine.

[0059] (2) Accuracy stability After 8 hours of continuous operation, the radial runout and axial runout of the correction roller 100 were tested again, and the changes were 0.0002 mm and 0.0003 mm, respectively, demonstrating excellent accuracy stability. This is because the tight fit clearance and stable lubrication condition prevented accuracy drift caused by component wear or increased clearance during long-term operation, verifying the effectiveness of the structural stability scheme in the claims.

[0060] The three embodiments correspond to three typical scenarios: conventional size, large diameter, and high speed and high vibration, respectively, verifying the versatility and adaptability of the technical solution of the present invention, and proving that the technical solution of the present invention can be flexibly adjusted according to different usage requirements, and can meet the accuracy and stability requirements.

[0061] The above description is only a preferred embodiment of the present invention and is not intended to limit the present invention. Any modifications, equivalent substitutions, or improvements made within the spirit and principles of the present invention should be included within the protection scope of the present invention.

Claims

1. A method of aligning a corrector, characterized by, It comprises the following steps: 1) Reference assembly: the scale ring (9) is sleeved on the small diameter section (11) of the main shaft (1), the inner hole of the scale ring (9) is matched with the small diameter section (11) in clearance, the eccentric structure worm wheel (4) is sleeved on the small diameter section (11), and the lower end surface of the worm wheel (4) is attached to the upper end surface of the scale ring (9); the correction roller (100) is matched with the worm wheel (4) through the inner hole, so that the lower end surface of the correction roller (100) is in abutment with the upper end surface of the worm wheel (4); the U-shaped frame (2) is fixed on the plane one (13) of the main shaft (1), and the worm (3) on the U-shaped frame (2) is engaged with the worm wheel (4), and the axis of the worm (3) is parallel to the axis of the main shaft (1); 2) Eccentric fine adjustment radial: the non-circular torsion driving part (31) of the driving tool is connected to the worm (3), the worm (3) is rotated to drive the worm wheel (4) to rotate around the small diameter section (11); the angle scale on the outer periphery of the scale ring (9) and the reference line (13) on the main shaft (1) are used to read the rotation angle of the worm wheel (4) and quantify the radial fine adjustment amount; the radial runout of the correction roller (100) is monitored in real time until the runout value is less than or equal to 0.002mm, and the self-locking characteristic of the worm (3) and the worm wheel (4) is used to lock the radial position; 3) Axial compensation: the end surface runout value of the correction roller (100) is measured, the scale ring (9) is rotated, the height difference between the upper end surface and the lower end surface of the scale ring (9) (the difference between the high point and the low point is less than or equal to 0.003mm) is used to make the high point of the scale ring (9) face the opposite direction of the axial deviation, and the end surface runout is compensated to be less than or equal to 0.002mm; 4) Fixing and balancing: the pressure plate (6) is covered on the upper end surface of the correction roller (100), the rod part of the large screw (5) passes through the through hole of the pressure plate (6) and is screwed with the screw hole (12) of the small diameter section (11), and the large screw (5) is tightened to realize the axial fixation of the worm wheel (4), the correction roller (100) and the scale ring (9); the counterweight (10) is installed on the plane two (14) of the main shaft (1), and the weight of the counterweight (10) is equal to the total weight of the U-shaped frame (2) and the worm (3), so as to balance the radial weight.

2. The method of aligning a corrector according to claim 1, wherein The eccentricity between the inner hole axis of the worm wheel (4) and the outer circle axis is 0.005-0.02mm in step 2), and the calculation method of the radial fine adjustment amount is: fine adjustment amount = eccentricity of worm wheel (4) x sinθ, wherein θ is the rotation angle of the worm wheel (4), and the reading accuracy of θ is 0.1°.

3. The method of aligning a corrector according to claim 1, wherein The matching method of the correction roller (100) and the worm wheel (4) in step 1) is that the correction roller (100) is sleeved on the outer peripheral wall of the sleeve (41) of the worm wheel (4), and the inner hole of the correction roller (100) is matched with the outer peripheral wall of the sleeve (41) in clearance; step 1) further comprises fixing the correction roller (100) and the worm wheel (4) by the small screw (7), specifically: the rod part of the small screw (7) passes through the axial countersunk through hole (101) of the correction roller (100) and is screwed with the axial small screw hole (42) of the worm wheel (4), and the head of the small screw (7) is sunk into the axial countersunk through hole (101).

4. The method of aligning a corrector according to claim 1, wherein The counterweight (10) and the U-shaped frame (2) are symmetrically distributed about the axis of the main shaft (1) in step 4) to reduce vibration when the main shaft (1) rotates, so that the vibration amplitude is ≤0.001mm.

5. A corrector alignment device, characterized by, Comprise: The main shaft (1): the upper end is coaxially reduced in diameter to form a small diameter section (11), a screw hole (12) coaxial with the small diameter section (11) is arranged at the center of the upper end surface of the small diameter section (11); the outer peripheral wall of the main shaft (1) is provided with a plane one (13) and a plane two (14) which are parallel to each other and symmetric about the axis of the main shaft (1); the outer peripheral wall of the main shaft (1) near the scale ring (9) is etched with a reference line (13) parallel to the axis of the main shaft (1); The eccentric fine adjustment assembly comprises a U-shaped frame (2), a worm (3) and an eccentric worm wheel (4); the U-shaped frame (2) is fixed on the plane one (13) by screws, and the two opposite vertical plates of the U-shaped frame (2) are provided with coaxial rotating holes (21), the axis of the rotating hole (21) is parallel to the axis of the main shaft (1); the worm (3) is rotatably arranged in the rotating hole (21), the lower end of the worm (3) is provided with a non-circular torsion driving part (31), the outer peripheral wall of the worm (3) is provided with an annular groove (32) corresponding to the outer side of the vertical plate of the U-shaped frame (2), an open annular snap spring (8) is clamped in the annular groove (32), and the outer diameter of the annular snap spring (8) is greater than the hole diameter of the rotating hole (21); the inner hole of the worm wheel (4) is in transition fit with the small diameter section (11), the eccentric distance between the axis of the inner hole of the worm wheel (4) and the axis of the outer circle is 0.005-0.02mm, the upper end of the worm wheel (4) is engaged with the worm (3), and the middle part of the worm wheel (4) extends upward along the axial direction to form an integrally formed sleeve (41), the inner cavity of the sleeve (41) is concentric with the inner hole of the worm wheel (4) and has the same hole diameter; The axial compensation assembly is the scale ring (9), which is sleeved on the small diameter section (11) and located below the worm wheel (4), and the inner hole of the scale ring (9) is in clearance fit with the small diameter section (11); the upper end surface and the lower end surface of the scale ring (9) are not parallel, and the difference between the high point and the low point is ≤0.003mm; the outer peripheral wall of the scale ring (9) is uniformly etched with an angular scale along the circumference, and the angular scale accuracy is 0.1°, which is used for aligning with the reference line (13) to quantify the rotation angle of the worm wheel (4); The axial fixing assembly comprises a pressure plate (6) and a large screw (5); the middle part of the pressure plate (6) is provided with a through hole matched with the rod part of the large screw (5), and the lower surface of the pressure plate (6) is used for abutting against the upper end surface of the correction roller (100); the rod part of the large screw (5) is threadedly connected with the screw hole (12) of the small diameter section (11) after penetrating through the through hole of the pressure plate (6); The dynamic balance assembly is the counterweight (10), which is fixed on the plane two (14) by screws, the weight of the counterweight (10) is equal to the total weight of the U-shaped frame (2) and the worm (3), and the counterweight (10) is symmetric about the axis of the main shaft (1) with the U-shaped frame (2). The connecting assembly: the correction roller (100) is uniformly provided with a plurality of axial countersunk through holes (101) along the circumference; the worm wheel (4) is provided with a plurality of axial small screw holes (42) corresponding to the axial countersunk through holes (101); further comprising a plurality of small screws (7), the rod part of the small screw (7) is respectively threaded through the axial countersunk through hole (101), and is threadedly connected with the axial small screw hole (42) one by one, and the head of the small screw (7) is sunk into the axial countersunk through hole (101).

6. The apparatus of claim 5, wherein, The outer peripheral wall of the sleeve (41) is used for cooperating with the inner hole of the correction roller (100), and the inner hole of the correction roller (100) and the outer peripheral wall of the sleeve (41) are gap matched, so as to form radial auxiliary positioning of the correction roller (100).

7. The aligner of claim 5 wherein, The engagement transmission of the worm (3) and the worm wheel (4) meets the self-locking condition, that is, the lead angle of the worm (3) is smaller than the equivalent friction angle between the meshing tooth surfaces, so as to lock the position of the worm wheel (4) after radial fine adjustment.

8. The aligner of claim 5, wherein The plane one (13) and the plane two (14) are both planes formed by the inward recess of the outer peripheral wall of the main shaft (1), and the recess depths of the two are consistent, so as to ensure that the installation height of the U-shaped frame (2) and the counterweight (10) is matched.

9. The aligner of claim 5, wherein The outer peripheral wall of the scale ring (9) is uniformly etched with angle scale in the range of ±90° along the circumference, and the angle scale accuracy is 0.1°, which is used for aligning with the reference line (13) to quantify the rotation angle of the worm wheel (4).

10. The aligner of claim 5, wherein The number of the small screw (7) is 4, and is equally spaced along the circumference of the correction roller (100), so as to ensure the stability of the coaxial fixation of the correction roller (100) and the worm wheel (4).

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