阅读说明：本技术 一种大输出转矩的光热工程定日镜驱动减速机 (Photo-thermal engineering heliostat driving speed reducer with large output torque ) 是由 刘思厚 黄怀斌 于 2019-12-16 设计创作，主要内容包括：一种大输出转矩的光热工程定日镜驱动减速机,包括高速级输入行星减速机、中间法兰盘、刚性盘、两件呈180°分布的摆线轮和输出轴,刚性盘与输出轴上分别安装有高精度角接触球轴承,高精度角接触球轴承的外侧安装于针齿壳的轴承孔内,刚性盘和输出轴与针齿壳间的轴承孔内设有经测量修磨过的大调整垫,大调整垫可以保证角接触轴承的预负荷,承担减速机外部的转矩、倾覆力矩、保持输出的平稳性等,输出轴的输出端中心部分密封有内包骨架封堵,输出轴与针齿壳间设有密封作用的X形橡胶密封圈,其作为输出轴转动时其与针齿壳间的密封,因输出轴运转较慢采用X形橡胶密封圈的胶圈结构即可实现可靠的双唇密封又可有效地减小密封结构所占空间。(A driving speed reducer of a heliostats in photo-thermal engineering with large output torque comprises a high-speed-level input planetary speed reducer, a middle flange plate, a rigid plate, two cycloidal gears and an output shaft which are distributed in 180 degrees, wherein high-precision angle contact ball bearings are respectively arranged on the rigid plate and the output shaft, the outer sides of the high-precision angle contact ball bearings are arranged in bearing holes of a pin gear shell, a large adjusting pad which is ground through measurement is arranged in the bearing holes between the rigid plate and the pin gear shell, the large adjusting pad can guarantee the preload of an angular contact bearing, bear the external torque and overturning moment of the speed reducer, keep the stability of output and the like, an inner bag framework plug is sealed at the central part of the output end of the output shaft, an X-shaped rubber sealing ring with sealing effect is arranged between the output shaft and the pin gear shell and used for sealing between the output shaft and the pin gear shell when the output shaft rotates, and reliable double-lip sealing can be realized and the sealing structure can be effectively Occupying space.)

1. A great output torque photothermal engineering heliostat driving speed reducer is characterized by comprising a high-speed input planetary speed reducer (16), a middle flange plate (13), a rigid plate (19), two cycloidal gears (22) and an output shaft (26) which are distributed in an angle of 180 degrees, wherein the two cycloidal gears (22) are arranged between the rigid plate (19) and the output shaft (26), the rigid plate (19) is connected with the output shaft (26), an input gear (18) is arranged on the output shaft of the planetary speed reducer (16), the input gear (18) penetrates through the middle flange plate (13) and is meshed with a group of planetary gears (4), the group of planetary gears (4) comprise three identical planetary gears (4), the three planetary gears (4) are uniformly distributed in the circumferential direction, the centers of the planetary gears (4) are involute internal splines, and the centers of the three planetary gears (4) are respectively provided with a crank shaft (5), the crankshaft (5) comprises concentric journals, eccentric journals and concentric journals which are sequentially connected, the crankshaft (5) is inserted in mounting holes of a rigid disc (19), two cycloidal gears (22) and an output shaft (26), tapered roller bearings (9) are respectively mounted on the two concentric journals on the crankshaft (5) and are respectively connected with the rigid disc (19) and the output shaft (26) through the tapered roller bearings (9), needle bearings (10) without inner and outer rings and with retainers are respectively mounted on the two eccentric journals on the crankshaft (5) and are respectively contacted with bearing holes of the two cycloidal gears (22) through the outer diameters of the needle bearings (10) without inner and outer rings and with retainers, the outer sides of the rigid disc (19) and the output shaft (26) are connected with a needle gear shell (23) through a middle flange plate (13), and a circle of needle gear pins (21) are circumferentially arranged on the needle gear shell (23), the two cycloid gears (22) are respectively meshed with the pin gears (21) in different directions, the center part of the output end of an output shaft (26) is sealed with an inner packing framework plug (7), an X-shaped rubber sealing ring (25) with a sealing function is arranged between the output shaft (26) and the pin gear shell (23), the X-shaped rubber sealing ring (25) is used for sealing the pin gear shell (23) when the output shaft (26) rotates, an O-shaped rubber sealing ring (12) is arranged between the pin gear shell (23) and the middle flange plate (13), and an O-shaped rubber sealing ring (17) with a fixed sealing function is padded between the middle flange plate (13) and a high-speed planetary reducer (16) which is arranged at a middle through hole of the middle flange plate (13) through a screw (15).

2. The solar-thermal engineering heliostat driving speed reducer with large output torque as recited in claim 1, wherein the rigid disk (19) and the output shaft (26) are precisely positioned by the internal thread taper pin (3) and are fastened together by the socket head cap screw (2) and simultaneously used as an output component.

3. The photothermal engineering heliostat driving speed reducer with large output torque according to claim 1, wherein the rigid disc (19) and the output shaft (26) are respectively provided with a high-precision angular contact ball bearing (24), the inner sides of the high-precision angular contact ball bearings (24) are respectively arranged in bearing holes at the periphery of the rigid disc (19) and the output shaft (26), the outer sides of the high-precision angular contact ball bearings (24) are arranged in bearing holes of the pin gear shell (23), and a large adjusting pad (20) which is ground by measurement is arranged in the bearing holes between the rigid disc (19) and the pin gear shell (23) and between the output shaft (26) and the pin gear shell (23).

4. The photothermal engineering heliostat driving speed reducer with large output torque according to claim 1, wherein a circlip for shaft (6) is arranged between the crank shaft (5) and the planetary gear (4), a spacer sleeve (14) is arranged on one side of the planetary gear (4) on the crank shaft (5), the circlip for shaft (6) and the spacer sleeve (14) are used for axially positioning the planetary gear (4) on the crank shaft (5), and the circlips for holes (11) are arranged in the mounting holes of the rigid disk (19) and the output shaft (26) on the crank shaft (5).

5. The photothermal engineering heliostat driving speed reducer with large output torque according to claim 1, wherein the pin gear housing (23) is integrally connected with a chassis, and the middle flange plate is a middle flange plate frame (27) with a lengthened middle part to form a Y-shaped speed reducer.

Technical Field

The invention relates to the technical field of speed reducers, in particular to a photothermal engineering heliostat driving speed reducer with large output torque.

Background

At present, the light-heat power generation project of 180m is utilized in developing green energy²The heliostat driving equipment is usually driven by a worm gear, the abrasion is fast, the service life is short, the repairing is difficult after the abrasion, the size is large, the efficiency is only about 20 percent when the heliostat driving equipment is used in photo-thermal engineering, the heliostat driving equipment is driven by a central transmission mode in the prior art, the transmission ratio is small, the bearing capacity is poor, the transmission return difference is large, the heliostat driving equipment is particularly not suitable for being applied under the working conditions of open air, large temperature difference and large gust, and the service life is short.

Disclosure of Invention

The invention aims to solve the problems and provides 180m with large transmission ratio, high bearing capacity, small return difference and high transmission efficiency, which has the maximum output torque of 54000 N.m and is suitable for being applied to the photo-thermal industry^{^2}The heliostat drives a speed reducer.

The technical scheme adopted by the invention is as follows:

a great output torque photothermal engineering heliostat driving speed reducer comprises a high-speed input planetary speed reducer, a middle flange plate, a rigid plate, two cycloidal gears and an output shaft which are distributed in 180 degrees, wherein the two cycloidal gears are arranged between the rigid plate and the output shaft, the rigid plate is connected with the output shaft, an input gear is arranged on the output shaft of the planetary speed reducer, the input gear penetrates through the middle flange plate and is meshed with a group of planetary gears, the group of planetary gears comprises three identical planetary gears which are uniformly distributed in the circumferential direction, the centers of the planetary gears are involute internal splines, a crankshaft is respectively arranged at the centers of the three planetary gears, the crankshaft comprises a concentric shaft neck, an eccentric shaft neck and a concentric shaft neck which are sequentially connected, the crankshaft is inserted into mounting holes of the rigid plate, the two cycloidal gears and the output shaft, conical roller bearings are respectively arranged on the two concentric shaft necks on the crankshaft, the crankshaft is connected with a rigid disc and an output shaft through tapered roller bearings, needle roller bearings without inner and outer rings and with retainers are respectively arranged on two eccentric shaft necks of the crankshaft and are respectively contacted with bearing holes of two cycloidal gears through the outer diameters of the needle roller bearings without inner and outer rings and with retainers, the outer sides of the rigid disc and the output shaft and a middle flange plate are connected with a needle gear shell, a circle of needle gear pins are circumferentially arranged on the needle gear shell, and the two cycloidal gears are respectively meshed with the needle gear pins in different directions.

The rigid disc and the output shaft are accurately positioned by the internal thread taper pin and are fastened into a whole by the hexagon socket head cap screw to be used as an output part.

The high-precision angular contact ball bearing is mounted on the rigid disc and the output shaft respectively, the inner sides of the high-precision angular contact ball bearing are mounted in bearing holes in the peripheries of the rigid disc and the output shaft respectively, the outer sides of the high-precision angular contact ball bearing are mounted in bearing holes in the pin gear shell, and large adjusting pads polished through measurement are arranged in the bearing holes between the rigid disc and the pin gear shell as well as between the output shaft and the pin gear shell.

The crankshaft is provided with an elastic check ring for the shaft between the crankshaft and the planetary gear, one side of the planetary gear on the crankshaft is provided with a spacing sleeve, the elastic check ring for the shaft and the spacing sleeve are used for axially positioning the planetary gear on the crankshaft, and the elastic check ring for the hole is arranged in the rigid disc and the output shaft mounting hole on the crankshaft and is used for axially positioning the rigid disc and the output shaft on the crankshaft. An X-shaped rubber sealing ring with sealing function is arranged between the output shaft and the pin gear shell, an O-shaped rubber sealing ring is arranged between the pin gear shell and the middle flange plate, and the O-shaped rubber sealing ring with fixed sealing function is arranged between the middle flange plate and the high-speed planetary reducer which is arranged at the middle through hole of the middle flange plate through a screw.

The central part of the output end of the output shaft is sealed with an inner bag framework plug, an oil filling hole which is used for dispensing oil seal to the central part is arranged on the output shaft, and the outer end of the oil filling hole is plugged with an outer plug screw.

And the tooth part is formed by optimizing the tooth shape of the part meshed with the pin gear pin on the periphery of the cycloidal gear.

The input gear, the planetary gear and the cycloidal gear all adopt hard tooth surfaces or an integral hardening structure.

The pin gear shell is integrally connected with a chassis, the middle flange plate is a middle flange plate frame with the middle part lengthened to form a Y-shaped speed reducer, and the speed reducer of the middle flange plate is a D-shaped speed reducer.

The invention has the beneficial effects that: the high-speed stage of the invention adopts a reliable power splitting mode, changes the traditional central transmission into peripheral transmission, changes and optimizes the weakest point of the original transmission mode, adopts a differential gear speed reducing mechanism, a cycloid tooth profile and one-tooth-difference transmission at an output part, can realize larger transmission ratio and smaller output power when being applied to the photo-thermal industry, is suitable for the working conditions of open air, large temperature difference, large gust and large sand dust which are required by the utilization of solar heat energy in the green energy industry, and can meet the requirements of working condition temperature of minus 30-60 ℃, large overturning moment and long service life.

Drawings

Fig. 1 is a schematic structural diagram of a D-type speed reducer according to the present invention.

Fig. 2 is a sectional view taken along line a-a in fig. 1.

FIG. 3 is an outline view of the D/Y type conjoined reducer of the present invention.

Wherein: 1-a plug screw; 2-socket head cap screw; 3-an internal thread taper pin; 4-a planetary gear; 5-crankshaft; 6-elastic retainer ring for shaft; 7-plugging an inner wrapping framework; 8-external screw plug; 9-tapered roller bearings; 10-needle roller bearing without inner and outer rings and with retainer; 11-circlip for hole; 12-O-shaped rubber sealing rings; 13-intermediate flange; 14-spacer sleeve; 15-screws; 16-a planetary reducer; 17-rubber sealing ring; 18-an input gear; 19-a rigid disc; 20-large adjustment pad; 21-a pin gear pin; 22-a cycloidal gear; 23-a needle gear shell; 24-angular contact ball bearings; 25-X-shaped rubber sealing rings; 26-an output shaft; 27-intermediate flange plate frame.

Detailed Description

A high-output-torque photothermal engineering heliostat driving speed reducer comprises a high-speed input planetary speed reducer 16, a middle flange plate 13, a rigid plate 19, two cycloidal gears 22 and an output shaft 26 which are distributed in a 180-degree manner, wherein the two cycloidal gears 22 are arranged between the rigid plate 19 and the output shaft 26, the rigid plate 19 is connected with the output shaft 26, an input gear 18 is installed on the output shaft of the planetary speed reducer 16, the input gear 18 penetrates through the middle flange plate 13 and is meshed with a set of planetary gears 4, the set of planetary gears 4 comprise three identical planetary gears 4, the three planetary gears 4 are uniformly distributed in the circumferential direction, the centers of the planetary gears 4 are involute internal splines, a crank shaft 5 is respectively installed at the centers of the three planetary gears 4, each crank shaft 5 comprises a concentric shaft neck, an eccentric shaft neck and a concentric shaft neck which are sequentially connected, and the crank shaft 5 is, In the mounting holes of the two cycloidal gears 22 and the output shaft 26, tapered roller bearings 9 are respectively mounted on two concentric shaft necks on the crankshaft 5 and are respectively connected with the rigid disc 19 and the output shaft 26 through the tapered roller bearings 9, needle bearings 10 without inner and outer rings and with retainers are respectively mounted on the two eccentric shaft necks on the crankshaft 5 and are respectively contacted with bearing holes of the two cycloidal gears 22 through the outer diameters of the needle bearings 10 without inner and outer rings and with retainers, needle gear shells 23 are connected with the outer sides of the rigid disc 19 and the output shaft 26 and the middle flange 13, a circle of needle gear pins 21 are circumferentially arranged on the needle gear shells 23, and the two cycloidal gears 22 are respectively meshed with the needle gear pins 21 in different directions, so that after the planetary gear 4 drives the crankshaft 5 to rotate for a circle, the cycloidal gears 16 rotate in opposite directions through being meshed with the needle gear pins 21 for a tooth pitch, and the speed. The internal shape structure of the D-type speed reducer is the same as the internal structure principle of the Y-type speed reducer, as shown in fig. 2, the high-speed stage adopts a reliable power splitting mode, changes the original central transmission into peripheral transmission, completely changes and optimizes the weakest point of the original transmission mode, and the output part adopts a differential gear speed reducing mechanism, a cycloid tooth shape and one-tooth-difference transmission. .

The rigid disc 19 and the output shaft 26 are accurately positioned by the internal thread taper pin 3 and are fastened into a whole by the socket head cap screw 2 and are used as output parts.

The rigid disc 19 and the output shaft 26 are respectively provided with a high-precision angle contact ball bearing 24, the inner sides of the high-precision angle contact ball bearings 24 are respectively arranged in bearing holes at the peripheries of the rigid disc 19 and the output shaft 26, the outer sides of the high-precision angle contact ball bearings 24 are arranged in bearing holes of the pin gear shell 23, large adjusting pads 20 which are ground through measurement are arranged in the bearing holes between the rigid disc 19 and the pin gear shell 23, and the large adjusting pads 20 can guarantee the preload of the angle contact ball bearings 24, bear the external torque and overturning moment of the speed reducer, keep the stability of output and the like.

A shaft elastic retainer ring 6 is arranged between the crank shaft 5 and the planetary gear 4, a spacer sleeve 14 is arranged on one side of the planetary gear 4 on the crank shaft 5, the shaft elastic retainer ring 6 and the spacer sleeve 14 are used for axially positioning the planetary gear 4 on the crank shaft 5, and holes 11 for elastic retainer rings are arranged in mounting holes of a rigid disk 19 and an output shaft 26 on the crank shaft 5 and are used for axially positioning the rigid disk 19 and the output shaft 26 on the crank shaft 5.

The central part of the output end of the output shaft 26 is sealed with an inner bag framework plug 7, an X-shaped rubber sealing ring 25 with sealing function is arranged between the output shaft 26 and the needle gear shell 23, the X-shaped rubber sealing ring 25 is used for sealing with the needle gear shell 23 when the output shaft 26 rotates, reliable double-lip sealing can be realized and the space occupied by a sealing structure can be effectively reduced by adopting a rubber ring structure of the X-shaped rubber sealing ring 25 because the output shaft rotates slowly, the O-shaped rubber sealing ring 12 is arranged between the needle gear shell 23 and the middle flange plate 13, the O-shaped rubber sealing ring 17 with fixed sealing function is arranged between the middle flange plate 13 and the high-speed planetary reducer 16 arranged at the middle through hole of the middle flange plate 13 through a screw 15, the common planetary reducer 16 is sealed by gluing through an end paper gasket, and when the connection end surface of the planetary reducer 16 adopts the mode of the O-shaped, not only improves the sealing reliability and reduces the cost, but also reduces the labor intensity.

The output shaft 26 is provided with an oil filling hole which is sealed by dispensing oil to the central part, the outer end of the oil filling hole is plugged with an outer plug 8, the middle flange plate 10 is provided with an oil drain hole, and the oil drain hole is internally provided with a plug 1.

The tooth profile of the meshing part of the periphery of the cycloid wheel 22 and the pin gear 21 is optimized to form a tooth profile, so that the requirement of instantaneous conjugate tooth number is met, and the basic conditions of high bearing capacity, high transmission precision and small transmission return difference are realized.

The input gear 18, the planetary gear 4 and the cycloid gear 22 all adopt hard tooth surfaces or an integral hardening structure, so that the requirements of less consumable materials, high efficiency and long service life of matching parts in the photo-thermal industry are met.

The pin gear shell 23 is integrally connected with a chassis, the middle flange plate is a middle flange plate frame 27 with the middle part being lengthened 13 to form a Y-shaped speed reducer, the speed reducer of the middle flange plate is a D-shaped speed reducer, and the D-shaped and the Y-shaped speed reducers are effectively connected in series according to the movement requirement of the heliostat.

D-shaped speed reducer and Y-shaped speed reducerCan be used independently, namely the output shaft is installed upwards or downwards for use and is installed horizontally for use, and can also be used for accurate operation of orientation and pitching motion of the heliostat in the photothermal engineering by using an D, Y model box combination, as shown in figure 3, so that the heliostat can be applied to 180m in the photothermal engineering²The heliostat drives a speed reducer, the main body part in an effective narrow space can reach 157, the total speed reduction ratio of a high-speed-level planetary speed reducer configuration mode can reach 47100, the large transmission ratio and the maximum output torque can reach 54000 N.m, the instantaneous maximum torque can reach 90000 N.m, the return difference is less than or equal to 1.5arc.min, and the characteristics of high bearing capacity and small return difference are realized; the transmission structure mode can adapt to the accurate control of two degrees of freedom of an azimuth drive D type and a pitching drive Y type of the photo-thermal engineering heliostat. The structure is not only suitable for the solar power generation industry of new energy, but also suitable for the use working conditions of large-scale traditional industrial robots, and because the series of the structures comprise the characteristic of large rated bearing capacity, the structure can be applied to the configuration of important joints of large and heavy industrial robots, and can fill the blank of products in the aspect of the market; in addition, the device can also be applied to high-bearing high-motion-precision mechanical transmission such as precision printing machinery, satellite tracking equipment, aerospace equipment, medical equipment, engineering machinery, military equipment and the like.

The embodiments of the present invention have been described in detail, but the description is only for the preferred embodiments of the present invention and should not be construed as limiting the scope of the present invention. All equivalent changes and modifications made within the scope of the present invention shall fall within the scope of the present invention.