CN113175497B - Transmission device for rotary table - Google Patents
Transmission device for rotary table Download PDFInfo
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- CN113175497B CN113175497B CN202110537602.0A CN202110537602A CN113175497B CN 113175497 B CN113175497 B CN 113175497B CN 202110537602 A CN202110537602 A CN 202110537602A CN 113175497 B CN113175497 B CN 113175497B
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H1/00—Toothed gearings for conveying rotary motion
- F16H1/02—Toothed gearings for conveying rotary motion without gears having orbital motion
- F16H1/04—Toothed gearings for conveying rotary motion without gears having orbital motion involving only two intermeshing members
- F16H1/12—Toothed gearings for conveying rotary motion without gears having orbital motion involving only two intermeshing members with non-parallel axes
- F16H1/16—Toothed gearings for conveying rotary motion without gears having orbital motion involving only two intermeshing members with non-parallel axes comprising worm and worm-wheel
- F16H1/163—Toothed gearings for conveying rotary motion without gears having orbital motion involving only two intermeshing members with non-parallel axes comprising worm and worm-wheel with balls between the co-operating parts
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H55/00—Elements with teeth or friction surfaces for conveying motion; Worms, pulleys or sheaves for gearing mechanisms
- F16H55/02—Toothed members; Worms
- F16H55/22—Toothed members; Worms for transmissions with crossing shafts, especially worms, worm-gears
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H57/00—General details of gearing
- F16H57/02—Gearboxes; Mounting gearing therein
- F16H57/023—Mounting or installation of gears or shafts in the gearboxes, e.g. methods or means for assembly
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- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
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- Gears, Cams (AREA)
Abstract
The invention relates to a transmission for a turntable, at least comprising a reduction gear, which comprises at least one worm, wherein the worm is formed by a first worm and a second worm, the annular worm teeth of the first worm and the second worm, which are respectively provided, are mirror-symmetrical with respect to a central region in abutment with one another, wherein a first left tooth flank of a first worm tooth, which changes substantially linearly, of the first worm can extend via a substantially plateau-shaped tooth tip into a first right tooth flank of a first worm tooth, which changes non-linearly, in particular substantially convexly, such that at least one right tooth flank of the first worm tooth, when the drive is activated, lies in line contact with a corresponding left roller flank of the worm wheel, and a second right tooth flank of a second worm tooth, which changes substantially linearly, of the second worm can extend via a substantially plateau-shaped tooth tip into a second left tooth flank of a second worm tooth, which changes non-linearly, in particular substantially convexly, so that the at least one second worm left flank bears in line contact against the corresponding roller right flank of the worm wheel when the drive action is effected.
Description
Technical Field
The invention relates to the technical field of numerical control rotary tables, in particular to a transmission device for a rotary table.
Background
The numerical control machine tool is often used for producing and processing parts with complex shape and structure, high requirement on batch large precision, short-period manufacture and the like, the numerical control rotary worktable is a common part on the numerical control machine tool, the numerical control rotary worktable is mainly used for fixing or supporting plate type and box type workpieces and carrying out continuous rotary processing and multi-surface processing on the plate type and the box type workpieces, the manufacturability can be enlarged and the processing time can be shortened by using the numerical control rotary worktable, and the numerical control rotary worktable can be used for feeding, indexing or reversing and the like of procedures such as boring, linear or planar milling or grinding and the like on the plate type and the box type workpieces.
CN107414510B discloses a numerical control rotary table with adjustable transmission ratio. The adopted technical scheme is as follows: a numerical control rotary table with adjustable transmission ratio comprises a driving motor, a rotary worm wheel and a speed reduction transmission device; the speed reduction transmission device comprises a driving worm connected with the driving motor through a length adjusting device and a transmission worm wheel meshed with the driving worm, a supporting shaft of the transmission worm wheel is fixedly connected with the sliding positioning block of the supporting plate, and the transmission worm wheel is fixedly connected with the transmission worm and has the same axis; one end of the transmission worm, which is far away from the transmission worm wheel, is meshed with the rotary worm wheel, and the axis of the rotary worm wheel is vertical to the axis of the driving worm; the total length of the length adjusting part and the driving worm and the position of the supporting shaft of the transmission worm wheel are determined by the diameter of the rotary worm wheel. The invention can adjust the transmission ratio and can more widely meet the requirements of different transmission ratios in practical application.
CN103111852A discloses a rotary table for a numerical control machine, comprising a box body, a front end cover, a rear end cover, a main shaft, a table surface, a three-gear-ring meshing mechanism, an oil cylinder and a driving mechanism for driving the main shaft to rotate, wherein the three-gear-ring meshing mechanism comprises an outer gear ring, an inner gear ring and a locking gear ring, the outer gear ring is fixedly connected with the front end cover, the inner gear ring is sleeved on the main shaft and is fixedly connected with the main shaft, the locking gear ring is sleeved on the main shaft through a gear ring inner sleeve, the front end cover and the rear end cover are both fixedly connected on the box body, the main shaft is rotatably supported on the front end cover and the rear end cover, the table surface is fixedly sleeved at one end of the main shaft, the oil cylinder is connected with the locking gear ring so that the locking gear ring axially moves on the main shaft to be engaged with or disengaged from the outer gear ring and the inner gear ring, the driving mechanism comprises a worm wheel component, a coupler and a motor, an output shaft of the motor is fixedly connected with one end of the worm through the coupler, the worm wheel assembly is sleeved on the main shaft. The transmission part of the invention has simple structure, omits intermediate transmission links, directly adopts the motor to drive the worm to rotate, improves the transmission precision and increases the transmission efficiency.
CN102168748B discloses a backlash-free worm gear and worm rotation speed reducing mechanism, wherein two pairs of worms in a box body are installed in an integral worm bearing eccentric sleeve, the two pairs of worms are respectively meshed with a middle output worm gear through flat and long openings of the eccentric sleeve on two sides, an input end drives a shaft gear to rotate in a meshing manner, the gear transmission system is connected with a gear holder and can be in radial linkage with the worms, an adjusting screw, a positioning frame and an automatic worm distance adjuster are connected and installed at an adjusting end, the initial gap of the inclined tooth surface at the meshing position of the worm gear and worm can be eliminated by rotating the adjusting screw through the positioning frame, the automatic worm distance adjuster can eliminate the subsequent meshing gap of the inclined tooth surface caused by mechanical abrasion during the operation of the mechanism, and backlash-free rotation output of the worm gear is realized through backlash-free meshing of the inclined tooth surface at the meshing position of the worm gear and worm gear. The invention can be widely applied to precise optical sighting, numerical control processing and servo control systems in the field of mechanical transmission as a non-backlash precise rotation and positioning actuating mechanism.
Although the numerical control rotary table provided by the prior art can be used for auxiliary processing of workpieces to a certain extent, the technical problems of low control precision of the rotary table, severe abrasion between teeth of the speed reducer, poor transmission efficiency of the speed reducer, large running noise of the rotary device, weak bearing capacity of the rotary table and the like still exist. Thus, there remains a need in the art for at least one or several aspects of improvement.
Furthermore, on the one hand, due to the differences in understanding to the person skilled in the art; on the other hand, since the inventor has studied a lot of documents and patents when making the present invention, but the space is not limited to the details and contents listed in the above, however, the present invention is by no means free of the features of the prior art, but the present invention has been provided with all the features of the prior art, and the applicant reserves the right to increase the related prior art in the background.
Disclosure of Invention
Aiming at the defects of the prior art, the invention provides a transmission device for a rotary table, which aims to solve at least one or more technical problems in the prior art.
To achieve the above object, the present invention provides a transmission device for a turntable, comprising at least: the speed reducer at least comprises a worm wheel and a worm, wherein a plurality of rollers are arranged on the circumferential outer side surface of the worm wheel in a clearance mode, the worm is provided with worm face and worm teeth matched with the rollers, and the servo driving device is used for driving the speed reducer to control the operation of the transmission device.
Preferably, the annular worm teeth of the first worm and the second worm are mirror-symmetrical with respect to a central portion where the first worm and the second worm are butted against each other. Forward rotation and reverse rotation are considered independently, and driving teeth adopted by forward rotation are different from driving teeth adopted by reverse rotation; the reason for this is because considering the actual use occasion, often will appear certain direction rotation drive obviously more than the rotation drive of another direction, for repair or change after the wearing and tearing, current left and right rotation separation's design can bring bigger replacement cost advantage. After adopting this design, spare part quantity obtains very big reduction.
Preferably, in a view taken along the worm axis, the first worm-tooth left flank of the first worm, which changes substantially linearly, can extend via a substantially plateau-shaped tooth crest to a first worm-tooth right flank, which changes non-linearly, in particular substantially crowning, such that at least one first worm-tooth right flank, when functioning as a drive, lies in line contact with a corresponding roller left flank of the worm wheel, and the second worm-tooth right flank of the second worm, which changes substantially linearly, can extend via a substantially plateau-shaped tooth crest to a second worm-tooth left flank, which changes non-linearly, in particular substantially crowning, such that at least one second worm-tooth left flank, when functioning as a drive, lies in line contact with a corresponding roller right flank of the worm wheel. The worm is divided into a left tooth and a right tooth which respectively bear a one-way driving task and has another unexpected technical effect, namely the ' leaning in a line contact way ' is necessary to provide for high-precision gapless transmission, not only extremely strict mathematical calculation is required, but also high-precision virtual fluted disc ' is required to simulate processing and actual processing, and the processing cost is extremely high; the left and right single-side driving mode of the invention determines that the high cost brought by the first worm tooth right tooth surface which is in non-linear change, in particular in approximately bulge shape, is not required to be used for the first worm tooth left tooth surface which is in linear change, thereby bringing great cost advantage.
Preferably, the diameter of the ring surface of the worm tooth of the worm is arranged in a manner of being nonlinearly changed in a direction towards two sides by taking the butt joint part of the first worm and the second worm as a center, so that the right tooth surface of the first worm tooth of the first worm is kept meshed with the left tooth surface of the roller of the worm wheel when correspondingly playing a driving action, and the left tooth surface of the second worm tooth of the second worm is kept meshed with the right tooth surface of the roller of the worm wheel when correspondingly playing the driving action.
Preferably, the gear flanks of the first worm and/or the second worm are formed with a conjugate movement envelope from different tooth profiles, and the tooth gaps between adjacent worm teeth of the first worm and/or the second worm can be adjusted by means of a corresponding spring tensioning device, preferably arranged at the interface of the first worm and the second worm.
Preferably, the worm wheel is rotatable following the rotation of the worm in a state where the roller thereof is kept meshed with the scroll teeth of the first and second worms, and the rotation axes and/or rotation planes of the worm wheel and the worm are different from each other, wherein the tooth widths of the annular scroll teeth provided to the first and second worms, respectively, are different from each other. So that the meshing gap between the worm teeth of the first and second worms and the rollers can be eliminated to the maximum.
Preferably, the roller of the worm wheel can form a meshing curved surface in space in a manner of meshing movement along with the worm, the meshing curved surface is a space envelope surface formed by a track envelope line formed by rotation of the roller around the axis of the worm wheel and rotation of the worm, and the rotation speed ratio of the worm wheel to the worm is the transmission ratio of the roller envelope speed reducer.
Preferably, the first worm and the second worm are asymmetrical to each other, wherein the first worm is mounted on the first worm from the outside by inserting its connecting shaft into the hollow channel of the second worm, wherein the ends of the first worm and the second worm, which are remote from the point of mutual abutment, are each provided with at least one step for mounting.
Preferably, the worm is provided at least one end with a worm gear connected to the servo drive, wherein the worm gear and the axis of rotation and/or the plane of rotation of the worm are coplanar with each other, and wherein the worm gear is capable of rotating the worm about its axis in such a way that the driving force of the servo drive is transmitted to the worm.
Preferably, a central rotating shaft is connected in the worm wheel, a connecting column is arranged on the central rotating shaft, the central rotating shaft drives the connecting column connected with the central rotating shaft to rotate coaxially in a mode of rotating along with the worm wheel, and the rotating axes and/or the rotating planes of the central rotating shaft and the worm are different from each other.
Preferably, the first worm and the second worm are in alternative contact to drive the roller of the worm wheel, so that the worm teeth of the first worm or the second worm are not in contact with the roller of the worm wheel at the same time during driving.
Preferably, the volute teeth at the abutting portion of the first worm and the second worm are formed by splicing half-teeth of the first worm and half-teeth of the second worm, wherein the splicing gaps are expanded along an involute in the circumferential direction, and two splicing gaps at two sides in the axial direction are located at positions staggered from each other. The worm face worm teeth formed by the two half worm teeth and positioned in the middle of the first worm and the second worm bear the largest roller rotating pressure, and the splicing gap is unfolded in an involute mode to effectively reduce the inter-tooth abrasion when the roller is meshed with the worm wheel teeth.
The beneficial technical effects of the invention comprise one or more of the following:
1. the special structure of the worm face and the worm teeth of the worm further improves the transmission efficiency of the worm and the worm gear and realizes ultra-silent operation, so that the rotary table has a series of advantages of high positioning precision, high transmission efficiency, ultra-silent operation and the like.
2. The worm is in a ring surface worm form, so that a plurality of worm wheel surface roller tooth surfaces are meshed with the worm wheel surface worm teeth of the worm at the same time, and the bearing capacity is greatly improved.
3. The left tooth surface and the right tooth surface of the sectional type worm adopt different types of driving teeth, and the design can bring greater replacement cost advantage.
Drawings
FIG. 1 is a schematic structural view of a preferred embodiment of a numerically controlled rotary table;
FIG. 2 is a preferred isometric view of a numerically controlled rotary table;
FIG. 3 is a right side view, preferably viewed in a first direction, of the perspective view shown in FIG. 2;
FIG. 4 is a top view, preferably viewed in a third direction, of the perspective view shown in FIG. 2;
FIG. 5 is a preferred isometric view of the worm;
FIG. 6 is a preferred machining schematic of the first worm;
FIG. 7 is a preferred cross-sectional view of the spiral wrap of the worm;
fig. 8 is a schematic partial cross-sectional view of the worm in engagement with the worm gear.
List of reference numerals
100: the speed reducer 101: the first rotating table 102: second rotating table
103: third rotating table 104: connecting column 105: worm wheel
106: the center rotating shaft 107: worm 108: worm gear
200: the fixing seat 201: fixing hole 300 a: first side fixing seat
300 b: second side holder 300 c: installation chamber 400: switching part
401: the movable portion 500: first numerical control turret 600: second numerical control rotary table
1071: first worm 1072: second worm 1073: volute face and volute teeth
71 a: first worm-tooth left tooth surface 71 b: first worm tooth right tooth surface 72 a: left tooth surface of second worm tooth
72 a: second worm right tooth surface 1074: step 1051: roller
1051 a: roller left tooth surface 1051 b: roller right tooth surface
Detailed Description
This is described in detail below with reference to fig. 1-8.
In the description of the present invention, it is to be understood that, if the terms "center", "longitudinal", "lateral", "length", "width", "thickness", "upper", "lower", "front", "rear", "left", "right", "vertical", "horizontal", "top", "bottom", "inner", "outer", "clockwise", "counterclockwise", etc. are used for indicating the orientation or positional relationship indicated based on the drawings, they are only for convenience of describing the present invention and simplifying the description, but do not indicate or imply that the device or element referred to must have a specific orientation, be constructed in a specific orientation and be operated, and thus, should not be construed as limiting the present invention.
In the description of the present invention, it should also be understood that "over" or "under" a first feature may include the first and second features being in direct contact, and may also include the first and second features being in contact not directly but through another feature therebetween, unless expressly stated or limited otherwise. Also, the first feature being "on," "above" and "over" the second feature includes the first feature being directly on and obliquely above the second feature, or merely indicating that the first feature is at a higher level than the second feature. A first feature being "under," "below," and "beneath" a second feature includes the first feature being directly under and obliquely below the second feature, or simply meaning that the first feature is at a lesser elevation than the second feature.
In the description of the present invention, it is to be understood that "first direction", "second direction" and "third direction" herein refer to: the axis X along the length direction of the fixing base 200 is the "first direction", the axis Y along the width direction of the fixing base 200 is the "second direction", and the axis Z along the height direction of the fixing base 200 is the "third direction".
The invention provides a transmission device for a rotary table, which can be arranged on a numerical control machine tool, and the transmission device can be shown in figures 1-4 as follows: a first numerical control turntable 500 for mainly carrying a workpiece and driving the workpiece to rotate; and a second numerically controlled turret 600 for controlling the rotation of the first numerically controlled turret 500 within the operating range. In addition, numerical control rotary table still includes: the fixing base 200 is provided with a plurality of fixing holes 201 on the surface thereof, the fixing base 200 can be installed on a numerical control machine tool through the fixing holes 201, a first side fixing base 300a and a second side fixing base 300b are fixedly installed at two ends of the fixing base 200, and the fixing base 200, the first side fixing base 300a and the second side fixing base 300b are combined to form a U-shaped framework of a workbench, wherein the first side fixing base 300a and the second side fixing base 300b can rotatably support the first numerical control rotary table 500 from two sides respectively, and a servo driving device in the second side fixing base 300b is used for driving the second numerical control rotary table 600.
According to a preferred embodiment, an adapter 400 is arranged on one side of the first side fixing seat 300a close to the middle of the workbench in the first direction along the workbench, and the adapter 400 is formed by combining an arc-shaped three-dimensional structure and a cubic structure. A rigid connecting shaft can be provided and/or connected near the central region of the adapter 400, which can be used for fastening and/or connecting the movable part 401. Further, the movable part 401 is plate-shaped, a plurality of connecting holes with different sizes are formed in the surface of the movable part, and the adapter part 400 is movably connected based on the matching relationship between the connecting shaft and the connecting holes in the movable part 401; on the other hand, the movable portion 401 can also be connected to the worm 107 located in the first numerical control turret 500 through a connection hole matching the diameter of the worm 107. Preferably, the movable part 401 can follow the rotation of the first numerical control turret 500 in the Y-Z plane to rotate on the connecting shaft of the joint 400 and the movable part 401, so that the movable part 401 can be fitted to the rotation of the first numerical control turret 500.
According to a preferred embodiment, the first side mount 300a rotatably supports and connects to the first numerical control turret 500 through the adapter 400 and the movable part 401, wherein the first numerical control turret 500 comprises a roller 1051 enveloping the reducer 100, see fig. 1. Specifically, the first numerically controlled turret 500 may be mounted and/or secured within the mounting chamber 300c, and the mounting chamber 300c may be fixedly coupled to the movable portion 401 via a threaded hole in the movable portion 401, see FIGS. 1-2.
According to a preferred embodiment, the roller 1051 envelope reducer 100 may include a worm 107 and a worm gear 105, see fig. 1. Alternatively, the worm 107 may be combined in segments, including a first worm 1071 and a second worm 1072, with the two segment worm having a special configuration of non-symmetrical spiral teeth 1073, see fig. 5 and 8. Preferably, one end of the first worm 1071 close to the second worm 1072 is provided as a connecting rod, such as a cylinder, see fig. 6. The second worm 1072 has a hollow passage such as a cylinder inside, and the inner diameter of the hollow passage matches the diameter of the connecting rod at one end of the first worm 1071. The second worm 1072 can be sleeved on the connecting shaft of the first worm 1071 through the hollow channel and move on the connecting shaft along a side close to the first worm 1071 so as to form a complete worm 107 with the first worm 1071. Preferably, respective spring tensioning means may be provided between adjacent worm face worm teeth 1073 of the first and second worms 1071, 1072 for adjusting the backlash of the two-stage worm. The ends of the first and second worm 1071 and 1072 remote from the point of abutment with each other are respectively provided with at least one step 1074 for assembly.
According to a preferred embodiment, the worm teeth 1073 of the first and second worms 1071, 1072 are respectively formed by the tooth surfaces of different tooth types of gears as generatrices through a conjugate motion envelope. Further, one end of the worm 107 is connected with at least one worm gear 108, and the worm gear 108 can be connected with a servo driving device such as a motor, so that the worm gear 108 can drive the worm 107 to rotate under the driving of the servo driving device. Alternatively, a servo driving means for controlling the rotation of the first numerical control turret 500 may be provided in the installation chamber 300c, see fig. 2. Specifically, the servo drive device can transmit a driving force to the worm 107 through the worm gear 108 to rotate the worm 107 along its axis, the worm 107 further transmits a force to the worm wheel 105 in contact with the worm 107 to rotate it, and the worm wheel 105 and the worm 107 are perpendicular to each other in the rotation axis space.
According to a preferred embodiment, in contact with the worm face teeth 1073 of the worm 107 and force transmission takes place through the disk-shaped worm wheel 105, see fig. 1. Specifically, the worm wheel 105 is surfaced with and/or attached to a number of rollers 1051. Preferably, the rollers 1051 may be distributed with some clearance on the annular side of the worm wheel 105. Preferably, the shape of the roller 1051 includes, but is not limited to, spherical, ellipsoidal, cylindrical, and the like. The rollers 1051 on the surface of the worm wheel 105 can be clearance-form-fitted with the worm teeth 1073 of the worm 107. Preferably, the worm 107 is in the form of a toroidal worm, and the first right tooth flank 71b of the worm gear 1073 on the first worm 1071 is kept in mesh with the left roller flank 1051a of the roller 1051 on the worm wheel 105, and the second left tooth flank 72a of the worm gear 1073 on the second worm 1072 is kept in mesh with the right roller flank 1051b of the roller 1051 on the worm wheel 105, thereby completely eliminating the backlash between the worm wheel 105 and the worm 107 during the forward and reverse rotation, see fig. 8. Particularly, the transmission mode of the worm wheel 105 and the worm 107 which are precisely attached has higher transmission efficiency and higher transmission precision, and meanwhile, the bearing capacity is greatly improved. Preferably, the roller 1051 is rotatable. The roller 1051 on the circumferential outer side surface of the worm wheel 105 and the worm gear 1073 of the worm 107 perform meshing motion to form a spatial meshing curved surface in space. The curved surface is characterized by a space envelope surface consisting of a track envelope line formed by the rotation of the roller 1051 around the axis of the worm wheel 105 and the rotation of the worm 107, and the rotating speed ratio of the two rotations is the transmission ratio of the worm wheel 105 and the worm 107.
Preferably, when the different-form worm-face worm teeth 1073 of the two worm segments shown in fig. 5 and 8 are processed, the specific form of the worm-face worm teeth 1073 of the two worm segments needs to be calculated by a formula according to parameters such as the number of worm heads, the number of teeth of the worm wheel, the center distance of the worm and the worm wheel, the height of the worm tooth top, the height of the worm tooth root, the height of the worm wheel tooth top, the height of the worm wheel tooth root, the sectional tooth form angle, the adjustment gap, and the like.
According to the gear meshing theory, a common normal vector of the tooth surfaces at a generated meshing point in the meshing process is orthogonal to a relative motion velocity vector of the tooth surfaces, namely, at the meshing point, the relative positions of the two meshing tooth surfaces along the direction of the common normal vector are kept static, and then a meshing equation of the two tooth surfaces at the meshing point can be obtained:
ν12·n＝0
wherein v is12Is the relative speed of movement of the engagement position and n is the common normal vector of the engagement position.
And projecting the relative speed vector at the meshing point to an n axis to obtain a meshing function of the transmission:
where Φ is the meshing function, M1、M2、M3Are all the coefficients of an equation,
starting angle of worm, c2Is the offset distance of the roller, A is the center distance, i21The rest parameters are related parameters of the roller motion coordinate system for the transmission ratio.
Further, the grinding wheel for grinding the worm 107 can be determined using the above parameters, while grinding of the worm face gear 1073 of the worm 107 can be achieved based on the relevant machining parameters at the time of machining. Further, the worm wheel 105 is machined by machining a hob of the same shape as the worm face worm teeth 1073.
Preferably, the left and right tooth surfaces of the roller of the worm wheel 105 are not formed by hobbing with one worm hob, but are formed by enveloping the left and right tooth surfaces of the two worm sections with their generatrices, respectively, so that when machining the corresponding worm wheel 105, it is necessary to first machine two hobs having parameters in accordance with the first worm 1071 and/or the second worm 1072, and then sequentially hobbing the left and right tooth surfaces of the roller of the worm wheel 105 with the two hobs, respectively. Further, the machining principle of the first worm 1071 and the second worm 1072 is the same, but the machining grinding wheel required for machining the first worm 1071 and the second worm 1072 is different, and it is necessary to adjust the gap between teeth and calculate the gap according to the actual application.
According to a preferred embodiment, in order to ensure that the first worm tooth right tooth surface 71b of the first worm 1071 is kept meshed with the roller left tooth surface 1051a of the worm wheel 105 and the second worm tooth left tooth surface 72a of the second worm 1072 is kept meshed with the roller right tooth surface 1051b of the worm wheel 105, the first worm 1071 and the second worm 1072 need to be ground by grinding wheels having the same shape during machining. Preferably, the first worm 1071 is taken as an example, see fig. 6. The left side of the grinding wheel is identical to that of a conventional double enveloping worm, and the right side of the grinding wheel is shifted compared with that of a conventional grinding wheel, so that the second worm 1072 is ground by a larger amount, and when finally meshing, the first worm tooth right flank 71b of the worm tooth 1073 on the first worm 1071 is meshed with only the roller left flank 1051a of the worm wheel 105. Preferably, the first worm 1071 rotates around the central axis of the worm 107 at the rotation speed w1, the grinding wheel rotates around the central axis of the worm wheel 105 at the speed w2, and the rotation speed w and the transmission ratio i of the two need to be in accordance with: w1/w2 ═ i, and the cutting process for the first worm 1071 is completed when the grinding wheel rotates at high speed about its own axis of rotation.
According to a preferred embodiment, a central rotating shaft 106 is connected to the inside of the worm wheel 105, and the central rotating shaft 106 is hollow and cylindrical, and a part of the shaft body extends outwards to one side of the worm wheel 105 along the axial direction. Further, the central rotation shaft 106 is connected with a connection column 104 having a cylindrical shape, see fig. 1. Further, the connecting column 104 is connected to a third rotating table 103. Preferably, the third rotation table 103 is connected to the first rotation table 101 and the second rotation table 102 at the top, wherein the second rotation table 102 is connected to the third rotation table 103 at the bottom and the second rotation table 102 is connected to the first rotation table 101 at the top. The first, second and third rotating tables 101, 102 and 103 have the same disk size, and the connecting column 104 and each rotating table rotate in the same direction with the central rotating shaft 106 as the rotating shaft.
According to a preferred embodiment, the second numerically controlled turret 600 may be mounted within a second side mount 300b located on the right side of the mount 200, see FIG. 2. The second side holder 300b is also provided therein with a servo driving device. Preferably, the servo driving device drives the worm 107 to rotate through the worm gear 108, so as to drive the worm wheel 105 to rotate. Further, the central rotating shaft 106 in the worm wheel 105 is driven by the worm wheel 105 to rotate, so that the connecting column 104 and the first, second and third rotating tables 101, 102 and 103 connected to the connecting column 104 rotate together, wherein the rotating centers of the worm wheel 105, the connecting column 104, the first, second and third rotating tables 101, 102 and 103 are the central rotating shaft 106.
Preferably, a common bearing structure is arranged in the mounting chamber 300c where the first numerical control rotary table 500 is located and/or the second side fixing base 300b where the second numerical control rotary table 600 is located for supporting and fixing the worm wheel 105, the worm 107, and various rotating tables and/or mounting tables. The installation surface of the first numerical control turntable 500 can be provided with various installation holes or installation grooves and the like which can be matched with the shape of a workpiece, and the installation holes or installation grooves can be used for fixing workpieces with complicated forms such as plate shapes, disc shapes and column shapes; the matched tailstock can be used for installing the machined parts of the rods and the shafts, so that the machining of the uniform and non-uniform continuous hole disc, the groove disc and the curved surface is realized, and the machining is shown in figure 2.
Preferably, the second numerical control turret 600 in the present embodiment is mainly used for controlling the rotation direction and/or speed of the first numerical control turret 500 in the Y-Z plane when the central rotating shaft 106 is used as the rotating shaft, and the second numerical control turret 600 may be connected to the installation chamber 300c where the first numerical control turret 500 is located in the middle of the working table, so that the first numerical control turret 500 can rotate in the Y-Z plane, and the movable portion 401 will rotate in the Y-Z plane by using the connecting shaft collinear with the central rotating shaft 106 as the rotating center in cooperation with the second numerical control turret 600, so that the workpiece on the installation surface of the first numerical control turret 500 can rotate in the Y-Z plane while rotating, as shown in fig. 1-2. Further, the workpiece on the first numerical control turret 500 may be subjected to machining in the form of cobalt, milling, boring, tapping, curved surface machining, and the like by a machining tool.
For ease of understanding, the principles of operation and method of use of a drive for a turntable of the present invention will be discussed.
In using the transmission provided according to the present application, a workpiece to be machined is secured to the mounting surface of the first numerically controlled turret 500 located in the middle of the table shown in fig. 1-2. Further, the corresponding servo drive is started by a control program of the system, a driving force of the servo drive is transmitted to the worm 107 after being decelerated by the worm gear 108, and the worm 107 rotates to further transmit the driving force to the worm wheel 105 to rotate. Secondly, the mounting table positioned at the top of the first numerical control rotary table 500 is driven by the rotation of the worm 107 and the worm wheel 105 to coaxially rotate, so that the workpiece to be processed positioned on the mounting table also rotates; meanwhile, under the driving of the servo driving device, the second numerical control rotary table 600 is matched with the movable part 401 positioned at the left side of the workbench to drive the first numerical control rotary table 500 positioned at the middle part to rotate in the Y-Z plane. During the rotation and/or rotation of the first numerically controlled turret 500, the machining tool may be used to perform machining processes such as cobalt, milling, boring, tapping, and surface machining on the workpiece.
According to the transmission device for the revolving platform, the roller envelope reducer is applied to the occasion of the numerical control revolving platform for the first time, and the traditional variable-lead worm gear transmission is replaced, so that the revolving precision of the numerical control revolving platform is greatly improved, wherein the special structure of the worm is different from the traditional worm gear reducer, so that the worm gear transmission structure has higher efficiency and higher transmission precision; the special structure of the worm gear teeth further improves the transmission efficiency of the worm gear and the worm and realizes ultra-silent operation, so that the rotary table has a series of advantages of high positioning precision, high transmission efficiency, ultra-silent operation and the like.
It should be noted that the above-mentioned embodiments are exemplary, and that those skilled in the art, having benefit of this disclosure, may devise various solutions which are within the scope of this disclosure and are within the scope of the invention. It should be understood by those skilled in the art that the present specification and figures are illustrative only and are not intended to be limiting on the claims. The scope of the invention is defined by the claims and their equivalents.
Claims (8)
1. A transmission for a turntable comprising at least:
-a reducer (100) comprising at least a worm wheel (105) and a worm (107), wherein,
a plurality of rollers (1051) are arranged in the gap of the circumferential outer side surface of the worm wheel (105), the worm (107) is provided with a worm face worm gear (1073) matched with the rollers (1051),
a servo drive for driving the reducer (100) to control the operation of the transmission,
it is characterized in that the preparation method is characterized in that,
the worm (107) is composed of a first worm (1071) and a second worm (1072), and the respective worm teeth (1073) of the first worm (1071) and the second worm (1072) are mirror-symmetrical with respect to a center portion where they are butted against each other,
in a view taken along the axis of the worm (107), a first, linearly changing worm tooth left flank (71 a) of the first worm (1071) can extend via a plateau-like tooth crest to a first, non-linearly changing worm tooth right flank (71 b) such that at least one first worm tooth right flank (71 b) bears in line contact against a corresponding roller left flank (1051 a) of the worm wheel (105) when the drive action is initiated, and a second, linearly changing worm tooth right flank (72 b) of the second worm (1072) can extend via a plateau-like tooth crest to a second, non-linearly changing worm tooth left flank (72 a) such that at least one second worm tooth left flank (72 a) bears in line contact against a corresponding roller right flank (1051 b) of the worm wheel (105) when the drive action is initiated;
Viewed along the axial direction of the worm (107), the diameter of the ring surface of the worm face worm teeth (1073) of the worm (107) is arranged in a manner of nonlinear change in the directions towards two sides by taking the abutting part of the first worm (1071) and the second worm (1072) as the center, so that the right tooth surface (71 b) of the first worm teeth (1071) is kept meshed with the left tooth surface (1051 a) of the worm wheel (105) when correspondingly playing the driving action, and the left tooth surface (72 a) of the second worm teeth (1072) is kept meshed with the right tooth surface (1051 b) of the worm wheel (105) when correspondingly playing the driving action;
the roller (1051) can rotate, the roller (1051) of the worm wheel (105) can form a meshing curved surface in space in a manner of meshing motion along with the worm (107), and the meshing curved surface is a space envelope surface formed by a track envelope line formed by the rotation of the roller (1051) around the axis of the worm wheel (105) and the rotation of the worm (107).
2. The transmission according to claim 1, characterized in that the worm-face worm-teeth (1073) of the first worm (1071) and/or the second worm (1072) are formed in a conjugate motion envelope with gear tooth faces of different tooth types as generatrices and the inter-tooth gap of adjacent worm-face worm-teeth (1073) of the first worm (1071) and/or the second worm (1072) can be adjusted by respective spring tensioning means provided at the abutment of the first worm (1071) and the second worm (1072).
3. The transmission according to claim 2, wherein the worm wheel (105) is rotatable following the rotation of the worm (107) in a state where the roller (1051) thereof is kept meshed with the worm face worm teeth (1073) of the first worm (1071) and the second worm (1072), and the rotation axes and/or the rotation planes of the worm wheel (105) and the worm (107) are different from each other, wherein the tooth widths of the annular worm face worm teeth (1073) provided to the first worm (1071) and the second worm (1072) respectively are different from each other.
4. Transmission according to claim 3, characterized in that said first worm screw (1071) and second worm screw (1072) are asymmetrical to each other, wherein said first worm screw (1071) is made to externally jacket said second worm screw (1072) on said first worm screw (1071) by inserting its connection shaft into the hollow channel of said second worm screw (1072),
wherein the ends of the first worm (1071) and the second worm (1072) remote from the point of mutual abutment are each provided with at least one step (1074) for assembly.
5. Transmission according to claim 4, characterized in that said worm (107) is provided at least one end with a worm gear (108) associated with a servo drive, wherein said worm gear (108) and the axis and/or plane of rotation of said worm (107) are coplanar with each other, said worm gear (108) being able to bring said worm (107) in rotation about its axis in such a way as to transmit the driving force of said servo drive to said worm (107).
6. Transmission according to claim 5, characterized in that a central rotating shaft (106) is connected in the worm wheel (105), a connecting column (104) is arranged on the central rotating shaft (106), the central rotating shaft (106) drives the connecting column (104) connected with the central rotating shaft to rotate coaxially in a manner of following the rotation of the worm wheel (105), wherein the rotating axes and/or rotating planes of the central rotating shaft (106) and the worm (107) are different from each other.
7. Transmission according to claim 6, characterized in that the first worm (1071) and the second worm (1072) are driving the roller (1051) of the worm wheel (105) in an alternative contact manner such that the worm face worm teeth (1073) of the first worm (1071) or the second worm (1072) do not contact the roller (1051) of the worm wheel (105) at the same time when driving.
8. The transmission according to claim 7, wherein the scroll teeth (1073) at the butt joint portion of the first worm (1071) and the second worm (1072) are split by half scroll teeth of the first worm (1071) and half scroll teeth of the second worm (1072), wherein split gaps are expanded in an involute curve in a circumferential direction, and two split gaps at both axial sides are located at positions shifted from each other.
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| CN202110537602.0A CN113175497B (en) | 2021-05-18 | 2021-05-18 | Transmission device for rotary table |
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| CN202110537602.0A CN113175497B (en) | 2021-05-18 | 2021-05-18 | Transmission device for rotary table |
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| CN113175497B true CN113175497B (en) | 2022-07-08 |
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| CN116044957A (en) * | 2023-04-03 | 2023-05-02 | 成都中良川工科技有限公司 | Roller envelope speed reducer with adjustable back clearance |
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