CN110802422A - Non-return difference machine tool rotary table - Google Patents
Non-return difference machine tool rotary table Download PDFInfo
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- CN110802422A CN110802422A CN201911089392.2A CN201911089392A CN110802422A CN 110802422 A CN110802422 A CN 110802422A CN 201911089392 A CN201911089392 A CN 201911089392A CN 110802422 A CN110802422 A CN 110802422A
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B23—MACHINE TOOLS; METAL-WORKING NOT OTHERWISE PROVIDED FOR
- B23Q—DETAILS, COMPONENTS, OR ACCESSORIES FOR MACHINE TOOLS, e.g. ARRANGEMENTS FOR COPYING OR CONTROLLING; MACHINE TOOLS IN GENERAL CHARACTERISED BY THE CONSTRUCTION OF PARTICULAR DETAILS OR COMPONENTS; COMBINATIONS OR ASSOCIATIONS OF METAL-WORKING MACHINES, NOT DIRECTED TO A PARTICULAR RESULT
- B23Q1/00—Members which are comprised in the general build-up of a form of machine, particularly relatively large fixed members
- B23Q1/25—Movable or adjustable work or tool supports
- B23Q1/26—Movable or adjustable work or tool supports characterised by constructional features relating to the co-operation of relatively movable members; Means for preventing relative movement of such members
Abstract
The invention relates to the technical field of machine tool turntables, in particular to a return difference-free machine tool turntable, which comprises: the device comprises a box body, a rotary table, a first transmission shaft and a second transmission shaft; the first gear is arranged on the first transmission shaft; the second gear is meshed with the first gear, and an inner gear ring is fixed on the inner wall of the second gear; the third gear is arranged on the second transmission shaft; a central shaft; the central wheel is rotatably arranged on the central shaft; the fourth gear is connected with the center wheel in a rotation stopping way and is meshed with the third gear; a third drive shaft; the planet wheel is arranged on the third transmission shaft in a rotation stopping way; the planet wheel is simultaneously meshed with the central wheel and the inner gear ring. Has the advantages that: when the rotary table is used, the first transmission shaft and the second transmission shaft do not need to rotate reversely, the rotation direction and the rotation speed of the rotary table can be changed by adjusting the rotation speed, each gear only rotates towards one direction, tooth surfaces can be always in contact, response is timely and rapid, a rotation gap does not exist, when the rotary table rotates forwards and backwards alternately, a rotation error is eliminated, and the rotation precision of the rotary table is improved.
Description
Technical Field
The invention relates to the technical field of machine tool turntables, in particular to a non-return-difference machine tool turntable.
Background
The precision rotary table is a key part of the machine tool, and the rotation precision of the rotary table determines the overall performance of the machine tool and the precision of a machined part. The existing common machine tool rotary tables comprise a worm gear rotary table, a direct-drive rotary table, a multi-stage gear transmission rotary table and the like, wherein the worm gear of the worm gear rotary table is worn quickly; although the direct-drive motor rotary table can achieve the purpose of high precision, the direct-drive motor has higher cost and smaller moment when the rotary table moves at low speed; in the process that the power input shaft of the multi-stage gear transmission rotary table rotates forwards or reversely to further realize the reverse rotation or the forward rotation of the rotary table, the multi-stage gear transmission can also rotate forwards or reversely, and due to the existence of the transmission chain gap, when the rotary table rotates forwards or reversely alternately, the rotation angle error reflected on the rotary table is larger, namely, the return difference exists.
As described above, since the above-described turn tables have high wear speed, a rotation gap, or a large reduction ratio motion transmission, and are high in manufacturing cost and poor in versatility, a high-precision turn table having a large transmission power, a large transmission ratio, and no backlash is required in accordance with the increasing demand for machining accuracy of machine parts.
Disclosure of Invention
The invention aims to provide a non-return-difference machine tool rotary table without a rotary gap.
In order to achieve the purpose, the non-return difference machine tool rotary table adopts the following technical scheme:
a non-return-difference machine turret comprising:
a box body;
the rotary table is rotatably arranged at the top of the box body, and the box body and the rotary table are enclosed to form an arrangement cavity for arranging the gear and the transmission shaft;
the first transmission shaft is rotatably arranged on the box body and is provided with a connecting end which is used for being in transmission connection with the first driving motor;
the second transmission shaft is rotatably arranged on the box body and is provided with a connecting end for transmission connection with a second driving motor, and the rotation directions of the second transmission shaft and the first transmission shaft are opposite when the second transmission shaft is used;
the first gear is arranged on the first transmission shaft and rotates synchronously with the first transmission shaft;
the second gear is rotatably arranged in the box body and is in meshing transmission with the first gear, an inner gear ring is fixed on the inner wall of the second gear or a circle of inner teeth is processed on the inner wall of the second gear, so that the first transmission shaft drives the inner gear ring or the inner teeth on the inner wall of the second gear to rotate through the meshing transmission of the first gear and the second gear;
the third gear is arranged on the second transmission shaft and synchronously rotates with the second transmission shaft;
the central shaft is fixedly matched with the box body and/or mutually rotationally matched with the rotary table, and the axis of the central shaft extends along the vertical direction;
the central wheel is rotatably arranged on the central shaft;
the fourth gear is in rotation stopping connection with the central wheel or is integrally arranged with the central wheel so as to synchronously rotate with the central wheel, and the fourth gear is in meshing transmission with the third gear, so that the second transmission shaft drives the central wheel to rotate through the meshing transmission of the third gear and the fourth gear;
a third drive shaft;
the planet wheel is arranged on the third transmission shaft;
the third transmission shaft is rotatably arranged on the rotary table, the planet wheel is rotatably mounted on the third transmission shaft or integrally arranged with the third transmission shaft so as to synchronously rotate with the third transmission shaft, or the third transmission shaft is fixedly mounted on the rotary table, and the planet wheel is rotatably mounted on the third transmission shaft;
the planet gear is in meshing transmission with the central gear and the inner gear ring at the same time, so that the planet gear, the inner gear ring, the central gear, the third transmission shaft and the rotary table form a planet gear mechanism, or the planet gear is in meshing transmission with the central gear and the inner teeth on the inner wall of the second gear at the same time, so that the planet gear, the inner teeth on the inner wall of the second gear, the central gear, the third transmission shaft and the rotary table form the planet gear mechanism.
The beneficial effects of the above technical scheme are that: the box body is rotatably provided with a first transmission shaft and a second transmission shaft, and the two transmission shafts are respectively in transmission connection with the driving motor, namely, the non-return-difference machine tool rotary table provided by the invention is provided with two power input shafts. Wherein the first transmission shaft drives the inner gear ring or the inner gear on the inner wall of the second gear to rotate through the meshing transmission of the first gear and the second gear, the second transmission shaft drives the central gear to rotate through the meshing transmission of the third gear and the fourth gear, and the planet gear, the inner tooth on the inner wall of the inner gear ring or the second gear, the central gear, the third transmission shaft and the turntable form a planet gear mechanism, so that the planet gear mechanism can have at most two input elements, and the rotation directions of the second transmission shaft and the first transmission shaft are opposite when in use, so if the first transmission shaft rotates anticlockwise and the second transmission shaft rotates clockwise, the first gear rotates anticlockwise and the second gear rotates clockwise, the inner gear ring or the inner gear rotates clockwise, so that the planet wheel is driven to rotate clockwise and generate a clockwise revolution trend, and the rotary table has a clockwise rotation trend; meanwhile, on the other side, the third gear rotates clockwise, the fourth gear rotates anticlockwise, and then the central wheel rotates anticlockwise, so that the planetary gear is driven to rotate clockwise and generate an anticlockwise revolution trend.
Therefore, the revolving stage specifically is clockwise rotation, still anticlockwise rotation, depends on the rotational speed size of ring gear or internal tooth and centre wheel completely, and who is bigger just rotates along with who, and then the rotation effect of output with it syntropy, consequently wants to realize the output of a certain direction of revolving stage and a certain rotational speed, only need to adjust the rotational speed of first transmission shaft and second transmission shaft can, this is more convenient the realization through first driving motor and second driving motor.
Of course, there is a certain condition that the rotating table does not rotate, the planet wheel does not produce revolution effect, and the rotating speed of the rotating table is zero at the moment. Of course, there are two extreme cases, one is that only the first transmission shaft rotates counterclockwise, the second transmission shaft does not rotate, at this time, the inner gear ring or inner gear of the planetary gear mechanism is used as an input element, the central wheel is used as a braking element, the planetary gear rotates clockwise + revolves clockwise, and then the turntable rotates clockwise, and at this time, the rotation speed of the turntable is maximum; in another case, only the second transmission shaft rotates clockwise, the first transmission shaft does not rotate, at this time, the central gear of the planetary gear mechanism serves as an input element, the inner gear ring or the inner gear teeth serve as a braking element, the planetary gear rotates clockwise and revolves counterclockwise, the turntable rotates counterclockwise, and the rotating speed of the turntable is also the maximum at this time.
Of course, if the first transmission shaft rotates clockwise and the second transmission shaft rotates anticlockwise, the principle is the same, so that the non-return-difference machine tool rotary table can output specific rotation direction and rotation speed only by controlling the rotation direction and rotation speed of the first transmission shaft and the second transmission shaft, and the rotation direction and rotation speed adjustment of the rotary table is very convenient.
And, the first transmission shaft and second transmission shaft each take its own role, after confirming its clockwise rotation or anticlockwise rotatory turn to, all need not the reverse rotation in the use, just can change the turn to and the rotational speed of revolving stage as long as adjust the rotational speed, that is to say, for the driving chain that the first transmission shaft drove, each gear only need rotate towards a direction, for the driving chain that the second transmission shaft drove, each gear also only needs to rotate towards a direction, all need not the reverse rotation (except that the revolving stage), therefore each flank of tooth can keep in touch all the time, there is not tooth side clearance, respond to in time rapidly, there is not the gyration clearance, the revolving stage is when corotation and reversal are alternated, there is not the corner error, the gyration precision of the revolving stage has been greatly improved, and then can improve the machining precision of part.
Furthermore, for convenience of manufacture and assembly and compact structure, the first transmission shaft and the second transmission shaft are arranged in parallel or coaxially, the axes of the first transmission shaft and the second transmission shaft are perpendicular to the axis of the central shaft, the axes of the first transmission shaft and the second transmission shaft are defined to extend along the left and right directions, and the first transmission shaft and the second transmission shaft are respectively positioned at the left side and the right side of the central shaft.
Further, for the convenience of installation, improve the stability of first transmission shaft and second transmission shaft, be provided with interior boss in the box, the one end of first transmission shaft and second transmission shaft all with box lateral wall rotational support cooperation, the other end all with interior boss rotational support cooperation.
Further, for the convenience of installing the third transmission shaft, the revolving stage includes the carousel and with carousel fixed connection's revolving stage body, the revolving stage body is located the top of carousel, carousel and box top rotation support cooperation, the third transmission shaft is installed on the carousel, is provided with the mounting hole that is used for installing the third transmission shaft on the carousel, the mounting hole is the through-hole.
Furthermore, for the convenience of installing the central shaft and the rotary table to be in mutual rotating fit, the rotary table is provided with a matching hole in rotating fit with the central shaft, and the matching hole is a through hole.
Drawings
FIG. 1 is a cross-sectional view of a turret of a non-return-difference machine tool according to the present invention;
FIG. 2 is a schematic diagram of the transmission of the turntable of the machine tool without backlash.
In the figure: 1-a first bearing; 2-a second bearing; 3-a first gear; 4-a first drive shaft; 5-a third bearing; 6-central axis; 7-a drive key; 8-a fourth bearing; 9-a box body; 10-a third gear; 11-a second drive shaft; 12-a fifth bearing; 13-a sixth bearing; 14-a second gear; 15-a seventh bearing; 16-turntable support bearings; 17-a turntable; 18-a turret body; 19-end cap; 20-bolt; 21-a fourth gear; 22-a central wheel; 23-eighth bearing; 24-a ninth bearing; 25-tenth bearing; 26-a third drive shaft; 27-a planet wheel; 28-ring gear; 29-inner boss.
Detailed Description
One embodiment of the non-return difference machine tool turntable of the invention is shown in fig. 1 and comprises a box body 9 and an end cover 19 fixed on the box body 9, wherein the end cover 19 is in a ring shape. The top of box 9 is rotated and is installed the revolving stage, and box 9 and revolving stage enclose to become to have the chamber of arranging that is used for arranging gear and transmission shaft, and the revolving stage in this embodiment includes carousel 17 and the revolving stage body 18 through bolt 20 and carousel 17 fixed connection, and revolving stage body 18 is located the top of carousel 17, and carousel 17 and box 9 top are through carousel support bearing 16 rotational support cooperation, and carousel support bearing 16 is plane thrust bearing.
The non-return difference machine tool rotary table comprises a central shaft 6 with an axis extending along the vertical direction, and the upper end of the central shaft 6 is rotatably arranged in the middle of the rotary table 17 through a ninth bearing 24. An inner boss 29 is integrally and convexly arranged on the bottom wall of the box body 9, the inner boss 29 is of a hollow structure, the bottom end of the central shaft 6 penetrates through the inner boss 29 and is inserted into the bottom wall of the box body 9, a step is arranged in the middle of the central shaft 6, and the step is matched with the top surface of the inner boss 29 in a blocking mode, so that the central shaft 6 is fixedly arranged relative to the box body 9.
Coaxial first transmission shaft 4 and second transmission shaft 11 are rotatably mounted on the side wall of the box 9 respectively, the axes of the first transmission shaft 4 and the second transmission shaft 11 extend along the left-right direction, and the axes of the first transmission shaft 4 and the second transmission shaft 11 are perpendicular to the axis of the central shaft 6, the first transmission shaft 4 is located on the right side of the central shaft 6, and the second transmission shaft 11 is located on the left side of the central shaft 6.
The right end of the first transmission shaft 4 is in rotary supporting fit with the side wall of the box 9 through the first bearing 1 and the second bearing 2, and the right end of the first transmission shaft is a connecting end for transmission connection with a first driving motor (not shown in the figure). The left end of the first transmission shaft 4 is in rotary supporting fit with the side wall of the inner boss 29 through the third bearing 5, so that the stability of the first transmission shaft 4 can be ensured, and the rigidity of the first transmission shaft is increased.
Similarly, the left end of the second transmission shaft 11 is rotatably supported and matched with the side wall of the box 9 through a fifth bearing 12 and a sixth bearing 13, and the left end thereof is a connection end for transmission connection with a second driving motor (not shown in the figure). The right end of the second transmission shaft 11 is in rotating supporting fit with the side wall of the inner boss 29 through the fourth bearing 8, so that the stability of the second transmission shaft 11 can be ensured, and the rigidity of the second transmission shaft can be increased.
The first transmission shaft 4 is connected with a first gear 3 which synchronously rotates in an up-and-down rotation mode, and the first gear 3 is a bevel gear. A second gear 14 is rotatably mounted in the box body 9 through a seventh bearing 15, the second gear 14 is in meshing transmission with the first gear 3, and the bottom of the second gear 14 is provided with an outer bevel gear in meshing transmission with the first gear 3, that is, the second gear 14 is also a bevel gear. The outer wall of the second gear 14 is matched with the seventh bearing 15, and the inner wall of the second gear is fixed with an inner gear ring 28, so that the first transmission shaft 4 can drive the inner gear ring 28 to rotate through the meshing transmission of the first gear 3 and the second gear 14.
The second transmission shaft 11 is connected with a third gear 10 which rotates synchronously in an up-and-down rotation mode, and the third gear 10 is a bevel gear. The center shaft 6 is rotatably provided with a center wheel 22 through an eighth bearing 23, the center wheel 22 is connected with a fourth gear 21 through a transmission key 7 in a rotation stopping way, so that the fourth gear 21 and the center wheel 22 rotate synchronously, the fourth gear 21 and the third gear 10 are in meshed transmission, and the fourth gear 21 is also a bevel gear, so that the second transmission shaft 11 can drive the center wheel 22 to rotate through the meshing of the third gear 10 and the fourth gear 21.
In the present embodiment, the fourth gear 21 is located inside the second gear 14, the meshing position of the second gear 14 and the first gear 3 is located on the right side of the central shaft 6, the meshing position of the fourth gear 21 and the third gear 10 is located on the left side of the central shaft 6, and the first transmission shaft 4 and the second transmission shaft 11 are coaxially arranged, so that the structural arrangement is relatively compact and the oversize of the machine tool rotary table is avoided.
The turntable 17 is rotatably provided with third transmission shafts 26 through tenth bearings 25, the number of the third transmission shafts 26 is more than two, and the third transmission shafts 26 are uniformly distributed around the central shaft 6 in a circumference manner. The mounting hole for mounting the third transmission shaft 26 on the rotary table 17 and the matching hole in running fit with the central shaft 6 are through holes, so that the third transmission shaft 26 and the central shaft 6 can be conveniently assembled.
The third transmission shaft 26 is provided with planetary gears 27 in an upper rotation mode, so that the planetary gears 27 and the third transmission shaft 26 rotate synchronously, the planetary gears 27 are in meshing transmission with the central gear 22 and the inner gear ring 28 simultaneously, and the planetary gears 27, the inner gear ring 28, the central gear 22, the third transmission shaft 26 and the rotary table form a planetary gear mechanism which can have at most two input elements.
When the non-return-difference machine tool turntable is used, the first transmission shaft 4 and the second transmission shaft 11 are both used as power input shafts, and the rotation directions of the first transmission shaft 4 and the second transmission shaft 11 are opposite, so that if the first transmission shaft 4 rotates anticlockwise (seen from right to left in fig. 1) and the second transmission shaft 11 rotates clockwise (seen from left to right in fig. 1), the first gear 3 rotates anticlockwise, the second gear 14 rotates clockwise, and the inner gear ring 28 rotates clockwise, so that the planet wheel 27 is driven to rotate clockwise and generate a clockwise revolution trend, and the turntable has a clockwise rotation trend; meanwhile, on the other side, the third gear 10 rotates clockwise, the fourth gear 21 rotates counterclockwise, and further the central wheel 22 rotates counterclockwise, so that the planet wheels 27 are driven to rotate clockwise and generate a counterclockwise revolution trend.
Therefore, the turntable specifically rotates clockwise or counterclockwise, which is completely determined by the rotation speed of the inner gear ring 28 and the central wheel 22, and who rotates along with the inner gear ring, and then outputs the same-direction rotation effect with the inner gear ring, so that the output of a certain direction and a certain rotation speed of the turntable is realized, and only the rotation speeds of the first transmission shaft 4 and the second transmission shaft 11 need to be adjusted, which is more conveniently realized through the first driving motor and the second driving motor.
Here, it is assumed that the number of teeth of the first gear 3 is Z1, the number of teeth of the second gear 14 is Z2, the number of teeth of the third gear 10 is Z3, the number of teeth of the fourth gear 21 is Z4, the number of teeth of the center gear 22 is Z5, the number of teeth of the planet gear 27 is Z6, the number of teeth of the ring gear 28 is Z7, the input rotation speed n1 (counterclockwise rotation) of the first transmission shaft 4, the input rotation speed n2 (clockwise rotation) of the second transmission shaft 11, the rotation speed of the turntable is n3, and with reference to fig. 2, the rotation speed of the fourth gear 21 is calculated as:
the rotational speed of the ring gear 28 is:
according to a differential gear train transmission ratio calculation formula:
obtaining the rotating speed of the rotary table:
when n3 is positive, the turntable rotates clockwise, and when n3 is negative, the turntable rotates counterclockwise. Of course, there is a certain condition that the turntable does not rotate, the planet wheels 27 do not produce a revolution effect, and the rotation speed of the turntable is zero at this time.
Of course, there are two extreme cases, one of which is that only the first transmission shaft 4 rotates counterclockwise, the second transmission shaft 11 does not rotate, the ring gear 28 of the planetary gear mechanism serves as an input element, the central wheel 22 serves as a braking element, the planetary wheels 27 rotate clockwise + revolve clockwise, and the turntable rotates clockwise, and the rotation speed of the turntable is at a maximum. The transmission ratio at this time is:
in another case, only the second transmission shaft 11 rotates clockwise, the first transmission shaft 4 does not rotate, the central gear 22 of the planetary gear mechanism serves as an input element, the ring gear 28 serves as a braking element, the planetary gears 27 rotate clockwise + revolve counterclockwise, and the turntable rotates counterclockwise, and the rotation speed of the turntable is also the maximum. The transmission ratio at this time is:
of course, if the first transmission shaft 4 rotates clockwise and the second transmission shaft 11 rotates counterclockwise, the principle is the same, and thus, the non-return-difference machine tool turntable can output specific rotation direction and rotation speed only by controlling the rotation direction and rotation speed of the first transmission shaft 4 and the second transmission shaft 11, and the rotation direction and rotation speed adjustment of the turntable is very convenient.
And, the first drive shaft 4 and the second drive shaft 11 each function, after confirming its clockwise rotation or anticlockwise rotatory turn to, all need not the reverse rotation in the use, just can change the turn to and the rotational speed of revolving stage as long as adjust the rotational speed, that is to say, for the drive chain that the first drive shaft 4 drove, each gear only need rotate towards a direction, for the drive chain that the second drive shaft 11 drove, each gear also only need rotate towards a direction, all need not the reverse rotation (except the revolving stage), therefore each flank of tooth can remain the contact all the time, there is not the tooth side clearance, respond to promptly and rapidly, there is not the gyration clearance, the revolving stage is when corotation and reversal are alternated, there is not the corner error, the gyration precision of the revolving stage has been improved greatly, and then can improve the machining precision of part.
In other embodiments of the machine tool rotary table without return difference, the central shaft and the rotary table are not in mutual rotating fit, the top end of the central shaft is a certain distance away from the rotary table, the central shaft and the rotary table are not in contact at all, the central shaft only needs to be in fixed fit with the box body at the moment, and the rotating center of the rotary table can be determined through the assembling relation of the rotary table and the box body at the moment.
In other embodiments of the non-return-difference machine turret, the central shaft is only in rotational engagement with the turntable, and not in fixed engagement with the housing.
In other embodiments of the non-return-difference machine turret, the turret is not a composite piece, but is a unitary part.
In other embodiments of the non-return-difference machine tool rotary table, no inner boss is arranged in the box body, and the first transmission shaft and the second transmission shaft are only in rotary supporting fit with the side wall of the box body.
In other embodiments of the non-return difference machine tool rotary table, the first transmission shaft can be arranged on the left side of the central shaft, the second transmission shaft is arranged on the right side of the central shaft, and the corresponding gear meshing position needs to be adjusted.
In other embodiments of the machine turret without backlash, when the first transmission shaft and the second transmission shaft are respectively positioned at the left side and the right side of the central shaft, the two shafts may not be coaxial, but arranged in parallel or designed in an intersecting manner.
In other embodiments of the non-return-difference machine tool rotary table, the first transmission shaft and the second transmission shaft may not be arranged in parallel or coaxially, for example, the first transmission shaft and the second transmission shaft may be arranged in a crossed manner with vertical axes, in which case the first gear and the second gear are meshed with each other, or the third gear and the fourth gear are meshed with each other.
In other embodiments of the non-return-difference machine tool rotary table, when the third transmission shaft is rotationally matched with the rotary table, the planet wheel and the third transmission shaft can also be integrally arranged, that is, the third transmission shaft is a gear shaft.
In other embodiments of the non-return-difference machine tool turntable, the third transmission shaft may be fixed on the turntable and cannot rotate relative to the turntable, and the planet wheel needs to be rotatably mounted on the third transmission shaft.
In other embodiments of the non-return-difference machine tool turret, the first gear and the first transmission shaft may be integrally provided, that is, the first transmission shaft is a gear shaft, and of course, the third gear and the second transmission shaft may also be integrally provided, and the second transmission shaft is also a gear shaft.
In other embodiments of the non-return-difference machine tool rotary table, the inner wall of the second gear is not fixed with an inner gear ring, but is provided with a circle of inner teeth, the inner teeth are meshed with the planet gears, and the inner teeth, the planet gears, the central gear, the third transmission shaft and the rotary table form a planet gear mechanism.
In other embodiments of the non-return difference machine tool rotary table, the fourth gear and the central wheel can be integrally arranged, so that synchronous rotation is realized.
Claims (5)
1. A non-return-difference machine tool turret, comprising:
a box body;
the rotary table is rotatably arranged at the top of the box body, and the box body and the rotary table are enclosed to form an arrangement cavity for arranging the gear and the transmission shaft;
the first transmission shaft is rotatably arranged on the box body and is provided with a connecting end which is used for being in transmission connection with the first driving motor;
the second transmission shaft is rotatably arranged on the box body and is provided with a connecting end for transmission connection with a second driving motor, and the rotation directions of the second transmission shaft and the first transmission shaft are opposite when the second transmission shaft is used;
the first gear is arranged on the first transmission shaft and rotates synchronously with the first transmission shaft;
the second gear is rotatably arranged in the box body and is in meshing transmission with the first gear, an inner gear ring is fixed on the inner wall of the second gear or a circle of inner teeth is processed on the inner wall of the second gear, so that the first transmission shaft drives the inner gear ring or the inner teeth on the inner wall of the second gear to rotate through the meshing transmission of the first gear and the second gear;
the third gear is arranged on the second transmission shaft and synchronously rotates with the second transmission shaft;
the central shaft is fixedly matched with the box body and/or mutually rotationally matched with the rotary table, and the axis of the central shaft extends along the vertical direction;
the central wheel is rotatably arranged on the central shaft;
the fourth gear is in rotation stopping connection with the central wheel or is integrally arranged with the central wheel so as to synchronously rotate with the central wheel, and the fourth gear is in meshing transmission with the third gear, so that the second transmission shaft drives the central wheel to rotate through the meshing transmission of the third gear and the fourth gear;
a third drive shaft;
the planet wheel is arranged on the third transmission shaft;
the third transmission shaft is rotatably arranged on the rotary table, the planet wheel is rotatably mounted on the third transmission shaft or integrally arranged with the third transmission shaft so as to synchronously rotate with the third transmission shaft, or the third transmission shaft is fixedly mounted on the rotary table, and the planet wheel is rotatably mounted on the third transmission shaft;
the planet gear is in meshing transmission with the central gear and the inner gear ring at the same time, so that the planet gear, the inner gear ring, the central gear, the third transmission shaft and the rotary table form a planet gear mechanism, or the planet gear is in meshing transmission with the central gear and the inner teeth on the inner wall of the second gear at the same time, so that the planet gear, the inner teeth on the inner wall of the second gear, the central gear, the third transmission shaft and the rotary table form the planet gear mechanism.
2. The non-return difference machine tool turntable according to claim 1, wherein the first transmission shaft and the second transmission shaft are arranged in parallel or coaxially, the axes of the first transmission shaft and the second transmission shaft are perpendicular to the axis of the central shaft, the axes of the first transmission shaft and the second transmission shaft are defined to extend in the left-right direction, and the first transmission shaft and the second transmission shaft are respectively positioned at the left side and the right side of the central shaft.
3. The returnless machine tool turret according to claim 2, wherein an inner boss is provided in the housing, and the first transmission shaft and the second transmission shaft are rotatably supported by the housing at one end and by the inner boss at the other end.
4. The non-return-difference machine tool turntable according to any one of claims 1 to 3, wherein the turntable comprises a turntable and a turntable body fixedly connected with the turntable, the turntable body is located above the turntable, the turntable is in rotating supporting fit with the top of the box body, the third transmission shaft is mounted on the turntable, a mounting hole for mounting the third transmission shaft is formed in the turntable, and the mounting hole is a through hole.
5. The non-return-difference machine tool turntable according to claim 4, wherein the central shaft and the turntable are rotatably engaged with each other, and the turntable is provided with a fitting hole rotatably engaged with the central shaft, and the fitting hole is a through hole.
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| Application Number | Priority Date | Filing Date | Title |
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| CN201911089392.2A CN110802422B (en) | 2019-11-08 | 2019-11-08 | Non-return difference machine tool rotary table |
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| CN201911089392.2A CN110802422B (en) | 2019-11-08 | 2019-11-08 | Non-return difference machine tool rotary table |
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Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN111593491A (en) * | 2020-04-23 | 2020-08-28 | 山东容润丰地毯有限公司 | Reversing mechanism, linear reversing device and lapping machine |
| CN113510492A (en) * | 2021-06-30 | 2021-10-19 | 深圳市蓝蓝科技有限公司 | High-speed numerical control rotary table of fourth shaft torque motor |
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| CN102230519A (en) * | 2011-04-12 | 2011-11-02 | 河南科技大学 | Face gear-type planetary reduction gearbox |
| CN203717797U (en) * | 2013-12-31 | 2014-07-16 | 天津百利天星传动有限公司 | Speed reducer with small return difference, large speed ratio and high accuracy |
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| CN113510492A (en) * | 2021-06-30 | 2021-10-19 | 深圳市蓝蓝科技有限公司 | High-speed numerical control rotary table of fourth shaft torque motor |
Also Published As
| Publication number | Publication date |
|---|---|
| CN110802422B (en) | 2021-07-16 |
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Application publication date: 20200218 Assignee: Luoyang kedager Transmission Research Institute Co.,Ltd. Assignor: HENAN University OF SCIENCE AND TECHNOLOGY Contract record no.: X2024980001766 Denomination of invention: A turntable for machine tools without backlash Granted publication date: 20210716 License type: Exclusive License Record date: 20240202 |