An eccentric mechanism for aligning a corrector

Abstract

The utility model discloses a correcting eccentric mechanism of aligning relates to mechanical aligning technical field, aims at solving the radial and end face runout error problem when correcting roller and main shaft cooperate. It includes the main shaft, and the small diameter section is equipped on the main shaft top, and the small diameter section cooperation eccentric worm wheel, and the worm wheel with correcting roller end face is fixed by abutting, and the U-shaped frame is fixed on the outer periphery of the main shaft, and the U-shaped frame is equipped with the worm that is parallel with the main shaft, and the worm is engaged with the worm wheel, and the worm wheel can be driven to drive the radial fine adjustment of correcting roller. Axial compression positioning can also be realized through the large screw and the pressure plate, and the end face runout is corrected through the precision gasket between the correcting roller and the worm wheel, and the worm rotation amount is quantified through the scale ring, and the radial eccentric weight is balanced through the counterweight. The mechanism can accurately adjust the position of the correcting roller, ensure the coaxial degree of the correcting roller and the main shaft, reduce the vibration, and is convenient to operate and stable in work, effectively improve the working precision of the correcting roller.

Description

Technical Field

[0001] This utility model relates to the field of machining technology, specifically to an eccentric mechanism for corrector alignment. Background Technology

[0002] In the grinding process of components, the dressing roller of the grinding wheel is a key component customized according to the workpiece. Its accuracy level directly affects the calibration quality of the grinding wheel profile, and thus determines the final machining accuracy of the workpiece. According to the machining requirements, the end face runout and radial runout of the dressing roller during installation must be controlled within 0.002mm. This accuracy standard is a core indicator to ensure grinding quality. From the perspective of actual production processes, although the correction roller is manufactured to the same precision standards and can meet the accuracy requirements for individual testing, accumulated errors will inevitably occur during the assembly process of installing it onto the machine tool roller drive shaft due to the fit between the shaft and the roller. These errors mainly originate from three aspects: first, the precision fit clearance between the drive shaft and the inner hole of the roller; second, the dimensional and positional tolerances inherent in the machine tool drive shaft system; and third, positioning deviations and uneven force distribution during assembly. These factors combined result in the correction roller often failing to consistently achieve the runout accuracy requirement of 0.002mm after conventional installation. Currently, the industry's solution to this problem mainly relies on operators repeatedly adjusting the rollers to find a suitable installation position. This process involves multiple disassemblies of the rollers, using measuring tools to check runout, and iterative adjustments to achieve the required accuracy. This traditional adjustment method has significant limitations: firstly, the repeated disassembly, measurement, and adjustment process is time-consuming and labor-intensive, severely impacting production efficiency; secondly, the adjustment effect is highly dependent on the operator's experience and skill level, resulting in poor consistency of adjustment results across different operating scenarios. This makes it difficult to guarantee the long-term stability of the correction roller installation accuracy, potentially leading to fluctuations in the grinding wheel correction quality and affecting the reliability of workpiece machining accuracy. Utility Model Content

[0003] To overcome any technical defects or shortcomings in existing technologies, this utility model provides a specialized mechanism capable of quickly, accurately, and stably achieving alignment and deflection self-centering of correction rollers, thus solving the problem of achieving accuracy standards due to accumulated errors during assembly in existing technologies. Therefore, the technical solution adopted by this utility model is as follows: An eccentric mechanism for corrector alignment includes a main shaft for engaging with and driving a correction roller to rotate. Unlike the prior art, the upper end of the main shaft is coaxially reduced in diameter to form a small diameter section, which is used to form a transition fit with a worm gear. A U-shaped frame is fixedly mounted on the outer peripheral wall of the main shaft near the small diameter section. A worm gear is rotatably mounted on the U-shaped frame, and the axis of the worm gear is parallel to the axis of the main shaft. The lower end of the worm gear is provided with a non-circular torsion drive part, which is used to connect an external drive tool to realize the rotation adjustment of the worm gear. The inner hole of the worm gear is transitionally fitted with the small diameter section of the main shaft, and the worm gear and the correction roller are coaxially fixedly connected by abutting their end faces. The worm gear meshes with the upper end of the worm, and the worm gear has an eccentric structure with an eccentricity of 0.005-0.02mm between its inner hole axis and outer circle axis. This allows the worm gear to drive the worm gear to rotate around the small diameter section of the main shaft, thereby driving the correction roller to achieve radial position fine adjustment relative to the main shaft.

[0004] Furthermore, a screw hole is provided at the center of the upper end face of the minor diameter section of the spindle, and the screw hole is coaxially arranged with the minor diameter section; It also includes a large screw and a pressure plate, wherein 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. 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. By tightening the large screw, the pressure plate can be driven to apply pressure downward along the main shaft axis, thereby achieving axial clamping and positioning of the correction roller and the worm gear.

[0005] Furthermore, the middle part of the worm gear extends upward along its own axis to form a sleeve, and the sleeve and the worm gear are integrally formed. The inner cavity of the sleeve is concentric with the inner hole of the worm gear and has the same diameter. The outer peripheral wall of the sleeve is used to mate with the inner hole of the correction roller. The correction roller is sleeved on the outer peripheral wall of the sleeve, and the inner hole of the correction roller and the outer peripheral wall of the sleeve are in clearance fit, so as to form radial auxiliary positioning of the correction roller through the sleeve.

[0006] Furthermore, the correction roller is provided with a plurality of axial countersunk holes evenly distributed along the circumference, and the axis of each axial countersunk hole is parallel to the axis of the correction roller. The worm gear has multiple small axial screw holes at the positions corresponding to the countersunk through holes in each axial direction, and the axis of each small axial screw hole is parallel to the axis of the worm gear. It also includes multiple small screws. The screw of each small screw passes through the axial countersunk hole of the correction roller and is threaded to the axial small screw hole of the worm gear. The head of the small screw is recessed into the axial countersunk hole to achieve coaxial fixed connection between the correction roller and the worm gear by abutting each other at the end faces.

[0007] Furthermore, a graduated ring is fitted on the minor diameter section of the main shaft below the worm gear, and the inner hole of the graduated ring is clearance-fitted with the minor diameter section. The upper and lower end faces of the scale ring are not parallel, and the difference between the high and low points is ≤0.003mm. By adjusting the angle of the scale ring relative to the main shaft, the height difference of its end faces is used to compensate for and correct the axial runout of the roller. The outer circumferential surface of the scale ring is uniformly etched with angle graduations along the circumference to indicate the rotation angle of the worm gear. On the outer circumferential surface of the main shaft near the scale ring, a reference line parallel to the main shaft axis is etched. The reference line is used to align with the angle scale on the scale ring to quantify the rotational adjustment of the worm gear relative to the main shaft.

[0008] Furthermore, the outer peripheral wall of the main shaft near the small diameter section is recessed inward to form a plane, and the U-shaped frame is fixed to the plane by screws.

[0009] Furthermore, a counterweight is fixedly mounted on the outer peripheral wall of the main shaft on the side radially opposite to the U-shaped frame; The counterweight and the U-shaped frame are symmetrically distributed about the axis of the main shaft to balance the radial imbalance caused by the U-shaped frame and the worm gear, thereby reducing vibration when the main shaft rotates.

[0010] Furthermore, the weight of the counterweight is equal to the total weight of the U-shaped frame and the worm gear, so as to achieve radial gravity balance of the main shaft.

[0011] Furthermore, the outer peripheral wall of the main shaft near the small diameter section is recessed inward to form a second plane, and the counterweight is fixed to the second plane by screws.

[0012] Furthermore, the two opposing upright plates of the U-shaped frame are respectively provided with coaxial rotating holes, and the axis of the rotating holes is parallel to the axis of the main shaft; The two ends of the worm are respectively inserted into two rotating holes, and the worm and the rotating holes form a rotational fit; On the outer sides of the two upright plates of the U-shaped frame, annular grooves are respectively opened on the outer peripheral wall of the worm gear, and an open annular retaining spring is inserted in each annular groove; The outer diameter of the ring snap ring is larger than the diameter of the rotating hole, which is used to limit the axial displacement of the worm and realize the axial positioning of the worm on the U-shaped frame.

[0013] The beneficial technical effects of this utility model are as follows: This technology enables precise adjustment of the radial runout of the correction roller. Through the eccentric structure of the worm gear and worm shaft, the worm gear rotates around the small diameter section of the main shaft, causing a slight radial displacement of the correction roller relative to the main shaft. This effectively eliminates accumulated errors generated during the interaction between the correction roller and the main shaft, ensuring that the radial runout meets high-precision installation requirements and providing a foundation for precise correction of the grinding wheel.

[0014] This design ensures reliable correction of the correction roller's end face runout. By utilizing the non-parallel design of the upper and lower end faces of the scale ring, the angle of the scale ring relative to the spindle is adjusted. The height difference of its end faces compensates for the axial runout deviation of the correction roller, ensuring the perpendicularity of the correction roller's end face to the spindle axis. This avoids the impact of end face runout on grinding accuracy and eliminates the need for additional shims, simplifying the adjustment assembly.

[0015] Improved ease and accuracy of adjustment operations. The angle scale on the outer circumference of the scale ring aligns with the baseline on the spindle, quantifying the rotational adjustment of the worm gear. This allows operators to intuitively grasp the adjustment range without repeated disassembly and measurement, reducing reliance on operational experience and improving self-aligning efficiency.

[0016] Enhance the stability and reliability of the mechanism's operation. The counterweight and U-shaped frame are symmetrically distributed about the axis of the main shaft, which can balance the radial imbalance generated by the U-shaped frame and worm gear, reducing vibration during main shaft rotation; the worm gear is axially positioned by a ring snap spring, and the pressure plate and large screw cooperate to axially press the correction roller and worm gear, effectively preventing component loosening and ensuring long-term stable operation of the mechanism.

[0017] Simplified assembly and maintenance process. Each component adopts a modular design. The correction roller is fixed to the worm gear with small screws and axially positioned with the pressure plate with large screws, making disassembly and assembly simple. When replacing the correction roller or maintaining the worm gear assembly, there is no need to make complex adjustments to the spindle and other core components, reducing maintenance difficulty and cost. Attached Figure Description

[0018] Figure 1 This is a schematic diagram of the structure of this utility model.

[0019] Figure 2 for Figure 1 A magnified view of a portion of the image.

[0020] Figure 3 for Figure 1 A sectional view.

[0021] Figure 4 for Figure 1 Partial diagram.

[0022] Figure 5 for Figure 1 Another perspective on the component separation. Detailed Implementation

[0023] In the description of this utility model, it should be noted that the terms "upper," "lower," "left," and "right" indicate the orientation or positional relationship based on the paper. This orientation or positional relationship is only for the convenience of describing this utility model and simplifying the description, and does 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 a limitation of this utility model.

[0024] In the description of this utility model, it should be noted that, unless otherwise explicitly specified and limited, the terms "installation," "connection," and "communication" 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 communication between two components. Those skilled in the art can understand the specific meaning of the above terms in this utility model based on the specific circumstances.

[0025] The following specific embodiments illustrate the implementation of this utility model. Those skilled in the art can easily understand other advantages and effects of this utility model from the content disclosed in this specification. Obviously, the described embodiments are only some, not all, of the embodiments of this utility model. Based on the embodiments of this utility model, all other embodiments obtained by those skilled in the art without creative effort are within the protection scope of this utility model.

[0026] An eccentricity mechanism for corrector alignment, such as Figure 1-5 As shown, the device includes a main shaft 1 for engaging and driving the rotation of a correction roller 100. The upper end of the main shaft 1 has a coaxially narrowed section 11, which is used to form a transition fit with a worm gear 4. A U-shaped frame 2 is fixedly mounted on the outer peripheral wall of the main shaft 1 near the small diameter section 11. A worm gear 3 is rotatably mounted on the U-shaped frame 2, and the axis of the worm gear 3 is parallel to the axis of the main shaft 1. The lower end of the worm gear 3 is provided with a non-circular torsion drive unit 31, which is used to connect an external driving tool to... The rotation adjustment of the worm gear 3 is achieved; the inner hole of the worm wheel 4 is transitionally fitted with the small diameter section 11 of the main shaft 1, and the worm wheel 4 and the correction roller 100 are coaxially fixedly connected by abutting their end faces; the worm wheel 4 meshes with the upper end of the worm gear 3 for transmission, and the worm wheel 4 has an eccentric structure, with an eccentricity of 0.005-0.02mm between its inner hole axis and outer circle axis, so that the worm gear 3 drives the worm wheel 4 to rotate around the small diameter section 11 of the main shaft 1, thereby driving the correction roller 100 to achieve radial position fine adjustment relative to the main shaft 1.

[0027] I. Core Principles This embodiment achieves fine-tuning of the radial position of the correction roller through the combination of "eccentric worm gear-worm meshing transmission" and "spindle reference positioning". The core logic is as follows: Component connection and reference relationship: The spindle is the core reference component. The small diameter section formed by the reduction of its upper end transitions with the inner hole of the worm wheel to ensure that the worm wheel can rotate stably around the small diameter section. The worm wheel and the correction roller are coaxially fixed by abutting their end faces. The worm is fixed to the outer peripheral wall of the spindle by a U-shaped bracket, and the axis of the worm is parallel to the axis of the spindle to ensure precise meshing between the upper end of the worm and the worm wheel.

[0028] Eccentric drive and fine-tuning logic: The worm gear has an eccentric structure. When the worm rotates, it drives the worm gear to rotate around the small diameter section of the main shaft through meshing transmission. Due to the eccentric characteristics of the worm gear, its outer circle will produce a slight radial offset with the rotation, which in turn drives the coaxial fixed correction roller to offset synchronously. Finally, the radial position of the correction roller relative to the main shaft is fine-tuned to eliminate radial runout error.

[0029] II. Actual Adjustment Process 1. Initial assembly and positioning: Fit the inner hole of the worm gear onto the small diameter section of the main shaft, so that the worm gear can rotate flexibly around the small diameter section; abut the correction roller against the end face of the worm gear and fix it coaxially to ensure that there is no relative displacement between the two; confirm that the worm is installed in place by the U-shaped bracket and maintains a meshing state with the upper end of the worm gear.

[0030] 2. Worm drive adjustment: Using an external drive tool, slowly rotate the worm; the worm drives the worm wheel to rotate around the small diameter section of the main shaft through meshing, and the outer circle of the worm wheel will be radially offset due to the eccentric structure, which will synchronously drive the correction roller to adjust the radial position.

[0031] 3. Precision monitoring and stop adjustment: During the rotation of the worm gear and worm wheel, the radial runout of the correction roller is monitored in real time. When the radial runout of the correction roller reaches the preset precision requirement, the worm gear is stopped. At this time, the radial position of the correction roller relative to the main shaft has been adjusted to a suitable state, and the fine adjustment is completed.

[0032] It should be noted that the meshing transmission between the worm and worm wheel has an inherent self-locking characteristic, which depends on the relationship between the worm's lead angle and the equivalent friction angle between the meshing teeth. When the worm's lead angle is smaller than the equivalent friction angle between the meshing tooth surfaces, the worm wheel cannot drive the worm to rotate in the opposite direction. In this mechanism, the worm needs to achieve "micro-precision adjustment," and its lead angle is designed to be a small angle, naturally satisfying the self-locking condition. Furthermore, the worm can only be rotatably mounted via a U-shaped bracket. After adjustment, even if the worm wheel rotates with the main shaft or is subjected to external forces, it cannot drive the worm to rotate. The worm can stably maintain its adjusted position, ensuring that the radial accuracy of the correction roller does not deviate.

[0033] In another preferred embodiment, a screw hole 12 is provided at the center of the upper end face of the small diameter section 11 of the main shaft 1, and the screw hole 12 is coaxially arranged with the small diameter section 11; it also includes a large screw 5 and a pressure plate 6, the pressure plate 6 has a through hole in the middle that is adapted to the shank of the large screw 5, and the lower surface of the pressure plate 6 is used to abut against the upper end face of the correction roller 100; the shank of the large screw 5 passes through the through hole of the pressure plate 6 and is threadedly connected to the screw hole 12 of the small diameter section 11. By tightening the large screw 5, the pressure plate 6 can be driven to apply pressure downward along the axial direction of the main shaft 1, thereby achieving axial clamping and positioning of the correction roller 100 and the worm gear 4. The core principle of this embodiment is to achieve axial tension adjustment and positioning of the correction roller and the worm gear through the cooperation of the large screw and the pressure plate. In the actual self-alignment process, first loosen the large screw to release the axial clamping force of the pressure plate on the correction roller and worm gear, eliminating the rotational constraint caused by the clamping. This allows the worm gear to rotate freely around the small diameter section of the main shaft, providing flexible movement space for the subsequent radial self-alignment driven by the worm. After the radial position is finely adjusted by rotating the worm, tighten the large screw to drive the pressure plate to apply stable pressure downward along the main shaft axis. This firmly fixes the relative position of the correction roller and worm gear, as well as the state of the worm gear on the main shaft, preventing the aligned components from shifting due to vibration or force. This ensures the stable maintenance of self-alignment accuracy and simplifies the fixing and unlocking process in self-alignment, improving operational convenience.

[0034] In another preferred embodiment, the middle part of the worm gear 4 extends upward along its own axial direction to form a sleeve 41, and the sleeve 41 and the worm gear 4 are integrally formed; the inner cavity of the sleeve 41 is concentrically arranged with the inner hole of the worm gear 4 and has the same diameter; the outer peripheral wall of the sleeve 41 is used to cooperate with the inner hole of the correction roller 100; the correction roller 100 is sleeved on the outer peripheral wall of the sleeve 41, and the inner hole of the correction roller 100 and the outer peripheral wall of the sleeve 41 are in clearance fit, so as to form radial auxiliary positioning of the correction roller 100 through the sleeve 41. The worm gear extends upward from the middle to form an integrally formed sleeve. The principle is that the inner cavity of the sleeve is concentric with the inner hole of the worm gear and the hole diameter is the same. The correction roller is sleeved on the outer peripheral wall of the sleeve with clearance fit. The sleeve can provide radial auxiliary positioning for the correction roller, further limiting the radial displacement of the correction roller, thereby improving the coaxiality between the correction roller, worm gear and spindle, making the connection between the three more stable and avoiding radial movement after self-alignment.

[0035] In another preferred embodiment, the correction roller 100 is provided with a plurality of axial countersunk holes 101 evenly distributed along the circumference, and the axis of each axial countersunk hole 101 is parallel to the axis of the correction roller 100; the worm gear 4 is provided with a plurality of axial small screw holes 42 corresponding to the positions of each axial countersunk hole 101, and the axis of each axial small screw hole 42 is parallel to the axis of the worm gear 4; it also includes a plurality of small screws 7, the screw portion of each small screw 7 passing through the axial countersunk hole 101 of the correction roller 100 and being threadedly connected to the axial small screw holes 42 of the worm gear 4 one-to-one, and the head of the small screw 7 is recessed into the axial countersunk hole 101, so as to realize the coaxial fixed connection between the correction roller 100 and the worm gear 4 by the end face abutment. An axial countersunk through hole is made in the correction roller, and an axial small threaded hole is made in the corresponding position of the worm gear. A small screw is used to fix it. The principle is that after the screw of the small screw passes through the countersunk through hole of the correction roller, it is threaded to the small threaded hole of the worm gear one by one. This makes the correction roller and the worm gear coaxially fixed by the end face abutting each other. At the same time, the head of the small screw is sunk into the countersunk through hole and will not protrude outward to interfere with other parts. This ensures the reliability of the fixation and avoids structural interference problems.

[0036] In another preferred embodiment, a scale ring 9 is fitted on the small diameter section 11 of the main shaft 1 below the worm gear 4. The inner hole of the scale ring 9 is clearance-fitted with the small diameter section 11. The upper and lower end faces of the scale ring 9 are not parallel, and the difference between the high and low points is ≤0.003mm. By adjusting the angle of the scale ring 9 relative to the main shaft 1, the height difference of its end face is used to compensate for and correct the axial runout of the roller 100. An angle scale is uniformly etched along the circumference on the outer circumferential surface of the scale ring 9 to indicate the rotation angle of the worm gear 4. A reference line 13 parallel to the axis of the main shaft 1 is etched on the outer circumferential surface of the main shaft 1 near the scale ring 9. The reference line 13 is used to align with the angle scale on the scale ring 9 to quantify the rotation adjustment of the worm gear 4 relative to the main shaft 1. This preferred embodiment uses a graduated ring with an inner hole that has a clearance fit on the minor diameter section of the main shaft. By utilizing the structural characteristic that the upper and lower end faces of the graduated ring are not parallel (the difference between the high and low points is ≤0.003mm), the axial runout of the correction roller can be compensated and corrected by adjusting the angle of the graduated ring relative to the main shaft through the height difference of its end faces. At the same time, the angle scale on the outer circumference of the graduated ring matches the reference line on the main shaft, which quantifies the rotation adjustment of the worm gear relative to the main shaft. This simplifies the adjustment components by eliminating the need for additional shims and achieves the dual functions of axial runout correction and adjustment range quantification, thereby improving the accuracy of self-alignment and ease of operation.

[0037] In another preferred embodiment, the outer peripheral wall of the main shaft 1 near the minor diameter section 11 is recessed inward to form a plane, and the U-shaped frame 2 is fixed to the plane by screws. This preferred embodiment utilizes the positioning stability of the planar structure to avoid the misalignment problem that easily occurs when the U-shaped frame is installed on a cylindrical surface, ensuring that the axis of the worm gear on the U-shaped frame remains parallel to the axis of the main shaft. This provides a structural foundation for the stable meshing of the worm gear and worm wheel, and reduces self-aligning errors caused by installation deviations.

[0038] In another preferred embodiment, a counterweight 10 is fixedly mounted on the outer peripheral wall of the main shaft 1 on the side radially opposite to the U-shaped frame 2. The counterweight 10 and the U-shaped frame 2 are symmetrically distributed about the axis of the main shaft 1, and are used to balance the radial imbalance generated by the U-shaped frame 2 and the worm gear 3, thereby reducing the vibration when the main shaft 1 rotates. This preferred embodiment, by installing a counterweight on the outer peripheral wall of the main shaft on the side radially opposite to the U-shaped frame, makes the counterweight symmetrically distributed with the U-shaped frame about the axis of the main shaft. The symmetrical structure balances the radial imbalance generated by the weight of the U-shaped frame and the worm gear itself, effectively counteracting the centrifugal force generated by the imbalance when the main shaft rotates, reducing the vibration amplitude of the main shaft, and ensuring the overall stability of the mechanism.

[0039] In another preferred embodiment, the weight of the counterweight 10 is equal to the total weight of the U-shaped frame 2 and the worm gear 3, so as to achieve radial gravity balance of the main shaft 1. This preferred embodiment achieves precise radial gravity balance of the main shaft by setting the weight of the counterweight to be equal to the total weight of the U-shaped frame and the worm gear, avoiding new imbalance problems caused by insufficient or excessive counterweight, further optimizing the uniformity of force during main shaft rotation, minimizing the impact of vibration on the working accuracy of the correction roller, and improving the reliability of the mechanism operation.

[0040] In another preferred embodiment, a second plane 14 is formed by an inward recess on the outer peripheral wall of the main shaft 1 near the small diameter section 11. The counterweight 10 is fixed to the second plane 14 by screws, and the second plane 14 is parallel to the first plane. This preferred embodiment, by forming a second plane by a recess on the outer peripheral wall of the main shaft, and fixing the counterweight to the second plane by screws so that the second plane is parallel to the first plane, utilizes the positioning characteristics of parallel planes to ensure more accurate symmetrical positioning of the counterweight and the U-shaped frame in the radial direction of the main shaft, avoiding counterweight installation misalignment that would disrupt the balance effect. At the same time, the planar structure facilitates quick positioning and installation of the counterweight, simplifying the assembly process.

[0041] In another preferred embodiment, two opposing upright plates of the U-shaped frame 2 are respectively provided with coaxial rotating holes 21, the axis of the rotating holes 21 being parallel to the axis of the main shaft 1; both ends of the worm 3 are respectively inserted into the two rotating holes 21, and the worm 3 and the rotating holes 21 form a rotational fit; corresponding to the outer side of the two upright plates of the U-shaped frame 2, annular grooves 32 are respectively provided on the outer peripheral wall of the worm 3, and an open-type annular retaining spring 8 is engaged in each annular groove 32; the outer diameter of the annular retaining spring 8 is larger than the diameter of the rotating hole 21, which is used to limit the axial displacement of the worm 3 and realize the axial positioning of the worm 3 on the U-shaped frame 2. This preferred embodiment involves creating coaxial rotating holes in the U-shaped frame and the upright plate, allowing the worm to pass through and form a rotating fit. Annular grooves are then created on the outer peripheral walls at both ends of the worm, and open-type annular retaining rings (with an outer diameter larger than the rotating hole diameter) are fitted into them. The retaining rings limit the axial displacement of the worm, achieving stable axial positioning of the worm on the U-shaped frame. This prevents axial movement of the worm during rotation adjustment or mechanism operation, ensuring the stability of the worm-worm wheel meshing. Furthermore, it eliminates the need for additional complex positioning structures, simplifying the design.

[0042] The above description is only a preferred embodiment of the present utility model and is not intended to limit the present utility model. Any modifications, equivalent substitutions, or improvements made within the spirit and principles of the present utility model should be included within the protection scope of the present utility model.

Claims

1. An eccentric mechanism for corrector alignment, comprising a main shaft (1) for engaging with and driving a corrector roller (100) to rotate, characterized in that, The upper end of the main shaft (1) is coaxially reduced to form a small diameter section (11), which is used to form a transition fit with the worm gear (4); A U-shaped frame (2) is fixedly mounted on the outer peripheral wall of the main shaft (1) near the small diameter section (11). A worm gear (3) is rotatably mounted on the U-shaped frame (2), and the axis of the worm gear (3) is parallel to the axis of the main shaft (1). The lower end of the worm (3) is provided with a non-circular torsion drive part (31), which is used to connect an external drive tool to realize the rotation adjustment of the worm (3). The inner hole of the worm gear (4) is transitionally fitted with the small diameter section (11) of the main shaft (1), and the worm gear (4) and the correction roller (100) are coaxially fixedly connected by abutting their end faces. The worm wheel (4) meshes with the upper end of the worm (3) for transmission, and the worm wheel (4) is an eccentric structure with an eccentricity of 0.005-0.02mm between its inner hole axis and outer circle axis. This allows the worm wheel (4) to rotate around the small diameter section (11) of the main shaft (1) via the worm (3), thereby driving the correction roller (100) to achieve radial position fine adjustment relative to the main shaft (1).

2. The eccentricity mechanism for corrector alignment according to claim 1, characterized in that, A screw hole (12) is provided at the center of the upper end face of the small diameter section (11) of the main shaft (1), and the screw hole (12) is coaxially arranged with the small diameter section (11); It also includes a large screw (5) and a pressure plate (6), wherein the pressure plate (6) has a through hole in the middle that is adapted to the rod of the large screw (5), and the lower surface of the pressure plate (6) is used to abut against the upper end face of the correction roller (100). After the shank of the large screw (5) passes through the through hole of the pressure plate (6), it is threaded to the screw hole (12) of the small diameter section (11). By tightening the large screw (5), the pressure plate (6) can be driven to apply pressure downward along the main shaft (1) to achieve axial clamping and positioning of the correction roller (100) and the worm gear (4).

3. The eccentricity mechanism for corrector alignment according to claim 1, characterized in that, The middle part of the worm gear (4) extends upward along its own axis to form a sleeve (41), and the sleeve (41) and the worm gear (4) are integrally formed. The inner cavity of the sleeve (41) is concentric with the inner hole of the worm gear (4) and has the same diameter. The outer peripheral wall of the sleeve (41) is used to cooperate with the inner hole of the correction roller (100). The correction roller (100) is sleeved on the outer peripheral wall of the sleeve (41), and the inner hole of the correction roller (100) and the outer peripheral wall of the sleeve (41) are in clearance fit so as to form radial auxiliary positioning of the correction roller (100) through the sleeve (41).

4. The eccentricity mechanism for corrector alignment according to claim 1, characterized in that, The correction roller (100) is provided with a plurality of axial countersunk holes (101) evenly distributed along the circumference, and the axis of each axial countersunk hole (101) is parallel to the axis of the correction roller (100). The worm wheel (4) is provided with multiple axial small screw holes (42) at the positions corresponding to each axial countersunk through hole (101), and the axis of each axial small screw hole (42) is parallel to the axis of the worm wheel (4). It also includes multiple small screws (7). The screw part of each small screw (7) passes through the axial countersunk through hole (101) of the correction roller (100) and is threadedly connected to the axial small screw hole (42) of the worm gear (4) one by one. The head of the small screw (7) is sunk into the axial countersunk through hole (101) so as to realize the coaxial fixed connection between the correction roller (100) and the worm gear (4) by the end face abutting.

5. The eccentricity mechanism for corrector alignment according to claim 1, characterized in that, On the small diameter section (11) of the main shaft (1), a scale ring (9) is also fitted below the worm gear (4), and the inner hole of the scale ring (9) and the small diameter section (11) are in clearance fit; The upper and lower surfaces of the scale ring (9) are not parallel, and the difference between the high and low points is ≤0.003mm. By adjusting the angle of the scale ring (9) relative to the main shaft (1), the axial runout of the correction roller (100) can be compensated by the height difference of its end face. The outer circumferential surface of the scale ring (9) is uniformly etched with angle scales along the circumferential direction to indicate the rotation angle of the worm gear (4); On the outer circumferential surface of the main shaft (1) near the scale ring (9), there is a reference line (13) parallel to the axis of the main shaft (1). The reference line (13) is used to align with the angle scale on the scale ring (9) to quantify the rotation adjustment of the worm gear (4) relative to the main shaft (1).

6. The eccentricity mechanism for corrector alignment according to claim 1, characterized in that, The outer peripheral wall of the main shaft (1) near the small diameter section (11) is recessed inward to form a plane, and the U-shaped frame (2) is fixed on the plane by screws.

7. The eccentricity mechanism for corrector alignment according to claim 1, characterized in that, On the outer peripheral wall of the main shaft (1), a counterweight (10) is fixed on the side that is radially opposite to the U-shaped frame (2). The counterweight (10) and the U-shaped frame (2) are symmetrically distributed about the axis of the main shaft (1) to balance the radial imbalance generated by the U-shaped frame (2) and the worm (3) and reduce the vibration when the main shaft (1) rotates.

8. The eccentricity mechanism for corrector alignment according to claim 7, characterized in that, The weight of the counterweight (10) is equal to the total weight of the U-shaped frame (2) and the worm gear (3) to achieve radial gravity balance of the main shaft (1).

9. The eccentricity mechanism for corrector alignment according to claim 7, characterized in that, The outer peripheral wall of the main shaft (1) near the small diameter section (11) is recessed inward to form a second plane (14), and the counterweight (10) is fixed on the second plane (14) by screws.

10. The eccentricity mechanism for corrector alignment according to claim 1, characterized in that, The two opposing upright plates of the U-shaped frame (2) are respectively provided with coaxial rotating holes (21), and the axis of the rotating holes (21) is parallel to the axis of the main shaft (1); The two ends of the worm (3) are respectively inserted into two rotating holes (21), and the worm (3) and the rotating holes (21) form a rotational fit; On the outer sides of the two upright plates of the U-shaped frame (2), the outer peripheral wall of the worm (3) is provided with annular grooves (32), and an open annular snap ring (8) is provided in each annular groove (32). The outer diameter of the ring snap ring (8) is larger than the diameter of the rotating hole (21), which is used to limit the axial displacement of the worm (3) and realize the axial positioning of the worm (3) on the U-shaped frame (2).

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