Machine tool index plate turbine worm transmission mechanism
By designing an eccentric bearing sleeve and adjusting the rotation angle, the problems of insufficient meshing accuracy and machining error in traditional worm gear transmission mechanisms are solved, achieving synergistic optimization of accuracy and cost, and making it suitable for high-precision machine tool indexing plates.
Patent Information
- Application Number
- CN202511244386.5
- Authority / Receiving Office
- CN · China
- Patent Type
- Applications(China)
- Current Assignee / Owner
- Filing Date
- 2025-09-02
- Publication Date
- 2025-11-07
AI Technical Summary
Traditional worm gear transmission mechanisms suffer from insufficient meshing accuracy, axial movement, and machining errors caused by frictional heat in high-speed and high-precision applications, and the machining cost of high-precision equipment is also high.
The eccentric bearing sleeve design automatically adjusts the shaft spacing between the worm and worm wheel by setting the inner and outer circles to be higher or lower and adjusting the rotation angle, thereby achieving dynamic compensation of the meshing clearance and reducing reliance on high-precision special equipment.
It improves the meshing accuracy and reliability of worm gears and reduces manufacturing costs. It is suitable for processing on ordinary standardized machine tools and meets high precision requirements.
Smart Images
Figure CN120901762A_ABST
Abstract
Description
TECHNICAL FIELD
[0001] The present application relates to the technical field of machine tool mechanical transmission, in particular to a machine tool index plate worm and gear transmission mechanism. BACKGROUND
[0002] As a core functional component of machine tools, the accuracy of the index plate directly determines the machining quality of the workpiece. The worm and gear mechanism is widely used in the precision indexing transmission of the index plate due to its large transmission ratio, good self-locking property, and strong carrying capacity.
[0003] However, as the requirements for machining precision and reliability in modern manufacturing continue to increase, the traditional worm and gear transmission mechanism has the problem of insufficient meshing accuracy, which can cause axial movement in high-speed and high-precision applications, leading to an increase in the circumferential cumulative error of the index plate and affecting the machining precision. Moreover, the friction heat between the worm and the turbine during long-term operation of the machine tool can cause the metal material to expand, further exacerbating the change in axial clearance. Currently, high-precision worm and gear transmission mechanisms require the use of high-cost special equipment for processing, which has the problem of high manufacturing cost.
[0004] In view of this, the present application has conducted in-depth research on the above-mentioned problems and proposed a high-precision worm and gear transmission mechanism for a machine tool index plate, thus generating the present application. SUMMARY
[0005] The present application aims to provide a machine tool index plate worm and gear transmission mechanism that achieves a synergistic optimization of precision, cost, and reliability.
[0006] To achieve the above-mentioned purpose, the solution of the present application is as follows:
[0007] A machine tool index plate worm and gear transmission mechanism, comprising a seat body, an axially perpendicular worm and worm gear, and a bearing sleeve arranged at the end of the worm; the bearing sleeve comprises an inner circle and an outer circle, the bearing sleeve is rotationally matched with the worm through the inner circle, and the bearing sleeve is rotationally matched with the mounting hole of the seat body through the outer circle and in a manner that can rotate around the outer circle axis at a preset angle; taking the axial direction of the worm as the high-low direction, the centers of the inner circle and the outer circle are arranged in a high-low eccentric manner.
[0008] The centers of the inner circle and the outer circle are arranged in a high-low eccentric manner, forming an eccentricity e, which satisfies: e = 0.01K, K being the axial distance between the worm and the worm gear.
[0009] The range of the eccentricity e is 1.2mm ≤ e ≤ 2.4mm.
[0010] The rotation preset angle θ satisfies: θ=(d×N÷R)×M; wherein, d is the diameter of the roller bearing arranged on the worm gear; N is the total number of the roller bearings arranged on the worm wheel; R is the radius of the worm wheel; and M is the meshing number of the roller bearing and the worm.
[0011] The preset angle θ ranges from 10° to 20°.
[0012] The high-low center direction of the inner circle and the outer circle is the reference direction, and the rotation preset angle is symmetrically distributed with the reference direction as the center line.
[0013] The bearing sleeve is provided with a plurality of long holes for defining the rotation angle, and the long holes are locked on the seat body by bolts.
[0014] The bearing sleeve is provided with a flange ring coaxial with the outer circle, and the plurality of long holes are circumferentially distributed on the flange ring.
[0015] The long holes are circumferentially distributed in eight.
[0016] The transmission mechanism further comprises a driving motor, a motor gear fixedly connected to an output shaft of the driving motor, a large gear meshing with the motor gear, a small gear fixedly connected coaxially with the large gear, and a worm gear fixedly connected coaxially with the worm and meshing with the small gear.
[0017] After the above scheme, the worm gear transmission mechanism of the machine tool index disc worm gear can automatically adjust the shaft spacing of the worm and the worm gear by the high-low eccentricity of the bearing sleeve inner circle and the outer circle during the operation of the transmission mechanism, realize the dynamic compensation control of the meshing gap, avoid the poor meshing caused by the cumulative machining error, and improve the meshing precision and reliability of the worm gear.
[0018] The cumulative machining error of the worm, the worm gear, the seat body and the like can be compensated by the rotation adjustment of the eccentric bearing sleeve, the high-precision machining is replaced by assembly compensation, the dependence on high-precision special equipment is reduced, that is, without relying on high-cost imported equipment, ordinary standardized machine tools can be used to machine parts, and the same performance can be achieved through assembly adjustment, and the manufacturing cost is greatly reduced. BRIEF DESCRIPTION OF DRAWINGS
[0019] Figure 1 is a structural schematic view of the basic index disc of the present application;
[0020] Figure 2 is Figure 1 a sectional view;
[0021] Figure 3 is Figure 1 a schematic view of the internal structure;
[0022] Figure 4 is a partial enlarged view of Figure 2 ;
[0023] Figure 5 is a schematic view of the bearing sleeve;
[0024] Figure 6 is a schematic view of the eccentric adjustment of the bearing sleeve Figure 1 ;
[0025] Figure 7 is a schematic view of the eccentric adjustment of the bearing sleeve Figure 2 .
[0026] Explanation of reference numerals
[0027] seat body 1, mounting hole 10, bolt hole 11; worm wheel 2, roller bearing 21; worm 3; bearing sleeve 4, inner circle 41, outer circle 42, long hole 43, flange ring 44; drive motor 51, motor gear 52, large gear 53, small gear 54, worm gear 55. DETAILED DESCRIPTION
[0028] The present case will be further described in detail in combination with specific embodiments.
[0029] The present case relates to a machine tool dividing disc worm gear transmission mechanism, as shown in the drawings, comprising a seat body 1, an axially perpendicular worm wheel 2 and worm 3, and a bearing sleeve 4 arranged at the end of the worm 3. Figures 1-3 The bearing sleeve 4 comprises an inner circle 41 and an outer circle 42, the bearing sleeve 4 is rotationally matched with the worm 2 through the inner circle 41, and the bearing sleeve 4 is rotationally matched with the mounting hole 10 of the seat body 1 through the outer circle 42 and in a manner that can rotate around the outer circle axis of the bearing sleeve 4 by a preset angle.
[0030] With the axial direction of the worm wheel 2 as the high-low direction (such as the vertical direction in the drawings), the center of the inner circle 41 and the center of the outer circle 42 are arranged in high-low eccentricity.
[0031] Figure 3
[0032] The present application discloses a dividing disc worm gear transmission mechanism, which is characterized by the high-low eccentricity of the inner circle 41 and the outer circle 42 of the bearing sleeve 4. When the transmission mechanism is in operation, the shaft spacing (center distance) between the worm gear 3 and the worm wheel 2 can be automatically adjusted by the rotation of the bearing sleeve 4, thereby achieving dynamic compensation control of the meshing gap, avoiding poor meshing caused by cumulative machining errors, and improving the meshing precision and reliability of the worm gear. The problem of tight meshing (jamming) or loose meshing (excessive backlash) caused by machining errors in the conventional single-sided bearing support structure of the worm gear is effectively solved. The worm gear with a single-sided bearing support is prone to axial floating when the load changes, and the present application can effectively suppress the axial movement of the worm gear during forward and reverse rotation.
[0033] The present application can compensate for the cumulative machining errors (such as center distance deviation and bearing hole coaxiality error) of the worm gear 3, the worm wheel 2, and the seat body 1 by the rotation adjustment of the eccentric bearing sleeve 4. By assembling compensation instead of high-precision machining, the dependence on high-precision special equipment is reduced, i.e., without relying on high-cost imported equipment, ordinary standardized machine tools can be used to machine parts, and the same performance can be achieved through assembly adjustment, thereby greatly reducing the manufacturing cost.
[0034] Therefore, the present application realizes the coordinated optimization of precision, cost, and reliability through the structural innovation of the eccentric bearing sleeve and the assembly process innovation of the rotation angle adjustment, and is particularly suitable for precise indexing equipment with high requirements for axial positioning precision and long-term transmission stability.
[0035] As shown in Figure 5 The center of the inner circle 41 and the center of the outer circle 42 are arranged with high-low eccentricity, forming an eccentric distance e, and the eccentric distance e satisfies: e = 0.01K, K is the shaft spacing (unit: mm) between the worm wheel 2 and the worm gear 3. The 1% proportional relationship between the eccentric distance e and the shaft spacing K is the optimal parameter verified by theoretical calculation and experiment, which can avoid over-tightening or over-loosening when adjusting the position of the worm gear 3, and ensure precise control of the meshing gap of the worm wheel. When the adjustment is too tight, i.e., the eccentricity is too large, the automatic adjustment range of the worm gear 3 is too large, which may cause the machine tool to jam and fail. When the adjustment is too loose, i.e., the eccentricity is too small, the machining error and assembly deviation cannot be effectively compensated, the meshing gap cannot be accurately controlled, and the machine tool precision requirement cannot be met.
[0036] The proportional formula of the eccentric distance can adapt to different specifications of the transmission mechanism. Regardless of the change of the shaft spacing of the worm gear, the eccentric distance can be dynamically adjusted by 1%. For example, the shaft spacing of the roller turbine and the worm gear is 121-315mm / 316-1000mm / 1001-4500mm, and the eccentric distance e is 1.21-3.15mm / 3.16-10mm / 10-45mm, respectively.
[0037] In a preferred embodiment, the eccentricity e is in the range of 1.2mm ≤ e ≤ 2.4mm. This range corresponds to a shaft spacing of 120-240mm, which can cover most application scenarios of machine tool indexing tables. For example... Figure 5 In a specific application example, the shaft spacing is 170mm and the design eccentricity is 1.7mm.
[0038] The bearing sleeve 4 can rotate around its outer circular axis by a preset angle, such as... Figures 2-5 As shown, the preset rotation angle θ satisfies: θ=(d×N÷R)×M; where d is the diameter (in mm) of the roller bearings 21 arranged on the worm gear 2; N is the total number of roller bearings 21 arranged on the turbine 2; R is the radius (in mm) of the turbine 2; and M is the number of times the roller bearings 21 mesh with the worm 3.
[0039] The d×N represents the overall dimensions of the roller bearing 21, and ÷R normalizes to the dimensions of the turbine 2 to ensure a reasonable proportion. ×M considers the actual number of meshing rollers and reflects dynamic load conditions, thus achieving a scientific parametric design to adapt to different specifications of mechanisms. In a preferred embodiment, the preset angle θ is in the range of 10°≤θ≤20°.
[0040] For example, in practical applications, the roller turbine 2 has a radius of 153.5 mm, and is designed with 24 roller bearings 21 (28 mm in diameter). The worm gear 3 meshes with 4 of the roller bearings 21. According to the formula, the rotation angle is 17.5 mm. Alternatively, with a roller turbine radius of 153.5 mm, it can be designed with 22 roller bearings 21 (30 mm in diameter), and the worm gear 3 meshes with 4 of the roller bearings 21. According to the formula, the rotation angle is 17.2 mm.
[0041] In a specific application example, the shaft spacing K is 170mm, the design eccentricity e is 1.7mm, the radius of the roller worm 2 is 153.5mm, 24 roller bearings 21 (diameter 28mm) are designed, the worm 3 meshes with 4 roller bearings 21, and the rotation angle θ is 17.5mm.
[0042] The bearing sleeve 4 of this invention, through the coordinated design of rotation angle and eccentricity, precisely matches the eccentricity and rotation angle according to the specific installation parameters of the worm gear, ensuring that the worm gear 3 and the turbine 2 form the optimal contact area after adjustment, avoiding local overload or excessive clearance, and greatly optimizing the performance of dynamic meshing adjustment.
[0043] Furthermore, such as Figure 5 As shown, the direction of the center of the inner circle 41 and the outer circle 42 is taken as the reference direction. Figure 5The rotation angle of the bearing sleeve 4 is locked by circumferentially distributed bolts (not shown in the figure), the bearing sleeve 4 is provided with a plurality of long holes 43 for limiting the rotation angle, the bolts pass through the long holes 43 and are locked on the seat body 1, and the seat body 1 is provided with bolt holes 11 for locking the bolts.
[0044] As shown in Figure 6 , the bearing sleeve 4 is counterclockwise rotated by θ / 2 (reverse rotation θ / 2), at this time, the eccentricity e1 is 1.68 mm (within the tolerance range), and the shaft spacing K1 is adjusted to 169.77 mm. As shown in Figure 7 , the bearing sleeve 4 is clockwise rotated by θ / 2 (forward rotation θ / 2), at this time, the eccentricity e2 is 1.68 mm (within the tolerance range), and the shaft spacing K2 is adjusted to 170.23 mm.
[0045] The rotation angle of the bearing sleeve 4 is locked by circumferentially distributed bolts (not shown in the figure), the bearing sleeve 4 is provided with a plurality of long holes 43 for limiting the rotation angle, the bolts pass through the long holes 43 and are locked on the seat body 1, and the seat body 1 is provided with bolt holes 11 for locking the bolts.
[0046] Further, the bearing sleeve 4 is provided with a flange ring 44 coaxial with the outer circle 42, and the plurality of long holes 43 are circumferentially distributed on the flange ring 44. The long hole 44 is provided with eight circumferentially distributed.
[0047] The long hole 44 on the bearing sleeve 4 cooperates with the bolt to realize stepless adjustment and accurate locking of the rotation angle. The circumferentially distributed long holes 44 make the bearing sleeve 4 bear force uniformly, avoid single-point stress concentration, and the use of eight circumferentially distributed long holes 44 and eight bolts makes the structure more stable and the adjustment more accurate.
[0048] As shown in Figure 2 , the transmission mechanism further includes a driving motor 51, a motor gear 52 fixedly connected to an output shaft of the driving motor 51, a large gear 53 engaged with the motor gear 52, a small gear 54 fixedly connected with the large gear 53 coaxially, and a worm gear 55 fixedly connected with the worm 3 coaxially and engaged with the small gear 54. The motor gear 52 is drivingly connected with the worm gear 55 via the large and small gears, forming multi-stage reduction, increasing the reduction ratio, and meeting the high requirement of the swing head on the torque.
[0049] The above only describes the preferred embodiments of the present application, and any equivalent changes and modifications made within the scope of the claims of the present application shall belong to the scope of the claims of the present application.
Claims
1. A machine tool dividing disc worm gear drive mechanism, characterized by: The transmission mechanism comprises a seat, a worm and a worm wheel which are perpendicular to each other in the axial direction, and a bearing sleeve arranged at the end of the worm; the bearing sleeve comprises an inner circle and an outer circle, the bearing sleeve is rotationally matched with the worm through the inner circle, and the bearing sleeve is rotationally matched with the mounting hole of the seat through the outer circle and in a manner that the outer circle can rotate by a preset angle about the outer circle axis; in the axial direction of the worm, the centers of the inner circle and the outer circle are arranged in a high-low eccentric manner.
2. A machine tool dividing plate worm and gear drive mechanism as claimed in claim 1, characterised in that: The centers of the inner circle and the outer circle are arranged in a high-low eccentric manner, forming an eccentricity e, and the eccentricity e satisfies: e=0.01K, K is the axial distance between the worm and the worm wheel.
3. A machine tool dividing plate worm and gear drive mechanism as claimed in claim 2, characterised in that: The eccentricity e ranges from 1.2mm to 2.4mm.
4. A machine tool dividing plate worm and gear drive mechanism as claimed in claim 1 or 2, characterised in that: The preset rotation angle θ satisfies: θ=(d×N÷R)×M; wherein d is the diameter of the roller bearing arranged on the worm wheel, N is the total number of the roller bearings arranged on the worm wheel, R is the radius of the worm wheel, and M is the number of meshing of the roller bearings and the worm.
5. A machine tool dividing plate worm and gear drive mechanism as claimed in claim 4 wherein: The preset angle θ ranges from 10° to 20°.
6. A machine tool dividing plate worm and gear drive mechanism as claimed in claim 4 wherein: The direction of the high-low centers of the inner circle and the outer circle is a reference direction, and the preset rotation angle is symmetrically distributed about the reference direction as a center line.
7. A machine tool dividing plate worm gear drive mechanism as claimed in claim 1, characterized in that: The bearing sleeve is provided with a plurality of long holes for limiting the rotation angle, and the long holes are locked on the seat by bolts.
8. A machine tool dividing plate worm and gear drive mechanism as claimed in claim 7 wherein: The bearing sleeve is provided with a flange ring coaxial with the outer circle, and the plurality of long holes are circumferentially distributed on the flange ring.
9. A machine tool dividing plate worm and gear drive mechanism as claimed in claim 7 or 8 wherein: The long holes are circumferentially distributed in eight.
10. A machine tool dividing plate worm and gear drive mechanism as claimed in claim 1, characterized in that: The transmission mechanism further comprises a driving motor, a motor gear fixedly connected to the output shaft of the driving motor, a large gear meshing with the motor gear, a small gear fixedly connected coaxially with the large gear, and a worm gear fixedly connected coaxially with the worm and meshing with the small gear.