Herringbone tooth planetary transmission speed reduction structure

Abstract

The invention belongs to the technical field of gear transmission, and relates to a planetary gear train structure, in particular to a herringbone tooth planetary transmission speed reduction structure. Comprising a sun gear, nP planetary gears, a first inner gear ring, a second inner gear ring, a planetary gear carrier, a planetary gear mounting disc, a planetary gear pin shaft, a planetary gear bearing, a locking nut, a connecting bolt, a spline housing, a pressing plate, a spacer sleeve, a positioning bush and a screw. Through the spline floating design of the sun gear and the inner gear ring, the uniform load adjusting effect when load distribution is not uniform due to error accumulation and the like in the working process of the herringbone tooth planetary mechanism can be achieved. The inner gear ring is designed into a split design and combination form of the first inner gear ring, the second inner gear ring, the planetary gear mounting disc, the planetary gear pin shaft and the planetary gear carrier, and the problem of assembly interference of herringbone tooth planetary transmission can be solved.

Description

Technical Field

[0001] The invention belongs to the technical field of gear transmission, relates to a planetary gear system configuration, and relates to a herringbone gear planetary transmission speed reduction structure. Background Art

[0002] At present, planetary gear transmission usually includes three transmission forms: spur gear, helical gear, and herringbone gear. The reducer mechanism using spur gear planetary transmission has limited output torque, poor transmission stability, large size, and high noise due to the low overlap of spur gear transmission. The reducer mechanism using helical gear planetary transmission will produce a large axial force. Compared with spur gear and helical gear planetary gear transmission, the herringbone gear planetary gear transmission uses a pair of helical gears with opposite rotation directions in a symmetrical configuration, which can further improve the load-bearing capacity of the reduction mechanism and offset the axial load acting on the bearing in the helical gear transmission, simplifying the axial support requirements of the gear, so that the gear can achieve error compensation and load distribution by its own force balance during the transmission process, greatly improving the transmission stability, and the system exhibits better noise characteristics. However, the use of herringbone gears also makes it difficult to install the sun gear, planetary gears and inner ring gears. In addition, due to the complex structure and working environment of the herringbone planetary gear transmission, in actual engineering applications, due to the influence of manufacturing errors, installation errors, flexible support and elastic deformation of components, the evenly distributed planetary gears produce vibrations, impacts, noise and other phenomena due to uneven loading, which seriously reduces the working performance, service life and reliability of the herringbone planetary gear transmission. Therefore, how to achieve the easy assembly of the herringbone planetary transmission reducer and the load-balancing characteristics between the planetary gears is an important problem that needs to be solved in the herringbone planetary transmission system. Summary of the invention

[0003] Purpose of the Invention

[0004] A herringbone planetary transmission reduction structure is provided, which can solve the problems of low overlap and low transmission power of spur planetary transmission and large axial force of helical planetary transmission, and solve the difficult assembly problem of herringbone planetary transmission, realize higher load-balancing characteristics between planetary wheels, obtain greater transmission power, compact transmission structure and higher transmission efficiency.

[0005] Technical Solution

[0006] A herringbone gear planetary transmission speed reduction structure, Figure 1 , including sun gear, n POne planetary gear, first internal gear ring, second internal gear ring, planetary gear carrier, planetary gear mounting disc, planetary gear pin shaft, planetary gear bearing, lock nut, connecting bolt, spline sleeve, pressing plate, spacer sleeve, positioning bushing, screw. The sun gear is connected to the internal spline shaft of the power input end through external spline A, inputting rotational speed and torque, and realizing the floating design of the sun gear through the reserved side clearance of the spline pair. The spline floating design plays a role in load adjustment, ensuring that the herringbone planetary gear train obtains a higher load sharing coefficient. The sun gear and the planetary gear are connected by herringbone tooth meshing to transmit the power input by the sun gear to the planetary gear. The planetary gear and the planetary gear carrier are tightly connected through the planetary gear pin shaft and the lock nut to further transmit the power of the planetary gear to the planetary gear carrier, realizing the output of rotational speed and torque. To solve the assembly problem of herringbone teeth, the sun gear is positioned by a support tooling. After the planetary gear bearing is installed in the inner hole of the planetary gear, n P The planetary gears are respectively inserted along the radial direction of the sun gear to make the herringbone teeth mesh, until it is ensured that the herringbone teeth of the sun gear and n P The planetary gears are located at the theoretical meshing position, and their positions are fixed. A planetary gear mounting disc is placed on the power input side of the planetary gear close to the sun gear. The planetary gear mounting disc is provided with mounting holes consistent with the number n P of planetary gears. The corresponding number of planetary gear pin shafts corresponding to the number n P of planetary gears respectively pass through the planetary gear mounting disc and the inner hole of the planetary gear bearing from the power input side of the sun gear, and are correspondingly inserted into the n P mounting holes provided on the planetary gear carrier. The inner hole position of the mating shaft section of the planetary gear pin shaft and the planetary gear carrier is provided with threads, and the lock nut is tightly connected to the internal threads of the planetary gear pin shaft to realize the integration of the planetary gear mounting disc, planetary gear, planetary gear bearing, and planetary gear carrier. The internal gear rings meshing with the herringbone teeth of the planetary gear are designed as a split-structured first internal gear ring and second internal gear ring. After the sun gear and the planetary gear are fixedly installed, the first internal gear ring and the second internal gear ring are respectively inserted from the two end faces of the planetary gear. After the first internal gear ring and the second internal gear ring are assembled and abutted, they are fixed into one body by connecting bolts to form a herringbone tooth ring. Spline B is designed on the outer sides of the first internal gear ring and the second internal gear ring to realize the floating connection of the herringbone tooth ring and improve the load sharing characteristics of the planetary mechanism. The first internal gear ring and the second internal gear ring are simultaneously connected to the spline sleeve through their respective spline B. One end of the spline sleeve is designed with a stop structure for limiting, and the other end is installed with a pressing plate for limiting. The spline sleeve and the pressing plate are both connected to the casing to realize the relative fixed design of the internal gear ring.

[0007] Furthermore, the machining accuracy of the tooth parts of the sun gear, planetary gear, first internal gear ring, and second internal gear ring should not be lower than grade 5.

[0008] Further, the external spline A on the sun gear is specifically an involute barrel spline, and the barrel amount is obtained through simulation analysis.

[0009] Further, the number of assembled planet gears n P is not less than 3, and a rolling bearing structure is required for installing the planet gear bearing in the inner hole.

[0010] Further, the planet gear carrier and the planet gear mounting disc need to be processed by a combined machining method for the machining of n P mounting holes to ensure the position accuracy of the mating holes with the planet gear pin shafts. For the combined machining method shown, the planet gear carrier is used as the machining reference, and positioning holes with the same number as the n P mounting holes are set on the planet gear carrier, evenly distributed between the n P mounting holes. After the mounting holes and positioning holes on the planet gear carrier are machined, n P positioning bushings and n P screw connection spacer sleeves are used to machine the positioning holes φC of the planet gear mounting disc and the n P spacer sleeves by a combined drilling method. After machining, n P positioning bushings and n P screws are installed to achieve precise positioning between the planet gear carrier and the planet gear mounting disc. Then, with φA on the planet gear carrier as the reference, the mounting hole φB on the planet gear mounting disc is machined to complete the combined machining among the planet gear carrier, the planet gear mounting disc and the planet gear pin shaft.

[0011] Further, the first internal gear ring 3 and the second internal gear ring 4 are of single helical tooth structure and need to be combined into a herringbone gear ring through connecting bolts 10. During machining, the first internal gear ring 3 and the second internal gear ring 4 are installed and combined after their respective rough machining, and positioning is achieved through positioning spigots. The positioning spigots are designed with a small-size transition fit, and combined machining is used to complete the grinding of the helical tooth surface, the machining of the spline and the bolt connection holes.

[0012] Further, short spline B structures are designed on the outer sides of the first internal gear ring and the second internal gear ring at positions symmetrical to the center of the herringbone gear. The stress state of the spline B tooth surface is determined through simulation analysis, and the requirements for tooth direction and tooth profile modification are given to ensure that no edge contact occurs during the meshing process of the spline pair.

[0013] Further, the spline sleeve is provided with a long spline C structure and meshes with the short spline B of the first internal gear ring and the second internal gear ring simultaneously. The spline sleeve is connected to the reducer housing body, and the connection method adopts general connection forms such as bolts and pre-set studs. A limiting edge is designed on the outer side end face side of the spline sleeve and the first internal gear ring, and a clearance structure is designed between the edge and the end face of the first internal gear ring, and the clearance is not less than 0.8 mm. A wear-resistant coating is applied to the side surface of the spline sleeve 11 close to the first internal gear ring 3.

[0014] Further, the pressing plate is installed on the outer end face of the second internal gear ring, with a clearance not greater than 0.8 mm from it, and a wear-resistant coating is applied to the side surface close to the second internal gear ring. The function of the pressing plate is the same as that of the spline sleeve edge.

[0015] The beneficial effects of this application are as follows:

[0016] A herringbone gear planetary transmission reduction structure proposed by the present invention provides a new configuration structure for the design of the planetary gear train in a reducer, and in particular can solve the design requirements for high-power transmission and high transmission efficiency in the reducer. Through the spline floating design of the sun gear and the internal gear ring, the equal load adjustment function can be realized when the load distribution is uneven due to error accumulation and the like during the operation of the herringbone gear planetary mechanism. The split design of the internal gear ring into the first internal gear ring 3 and the second internal gear ring 4, and the split design and combination form of the planetary gear mounting disc, the planetary gear pin shaft, and the planetary gear carrier can solve the assembly interference problem of the herringbone gear planetary transmission. The combination processing technology is adopted for the herringbone gear tooth profile and the positioning structure of the first internal gear ring 3 and the second internal gear ring 4, and the combination processing technology is adopted for the planetary gear carrier and the planetary gear mounting disc, which can ensure the processing accuracy of the components of the herringbone gear planetary transmission and the installation accuracy of the components. Finally, the assemblability and high equal load performance of the herringbone gear planetary transmission reducer design are realized. Description of the Drawings

[0017] Figure 1 Schematic diagram of the herringbone gear planetary transmission reduction mechanism;

[0018] Figure 2 Combined processing state diagram of the planetary gear carrier 5, the planetary gear pin shaft 7, and the planetary gear mounting disc (different perspectives);

[0019] Figure 3 Combined processing state diagram of the internal gear ring 3 and the internal gear ring 4. Detailed Embodiment

[0020] To make the purpose, technical solution, and advantages of the implementation of the present invention clearer, the technical solutions in the embodiments of the present invention will be described in more detail below. In the examples, the same or similar reference numerals represent the same or similar components or components with the same or similar functions throughout. The described embodiments are some, but not all, of the embodiments of the present invention. The following described embodiments by reference are exemplary and are intended to explain the present invention and should not be construed as limiting the present invention. All other embodiments obtained by those of ordinary skill in the art based on the embodiments of the present invention without creative efforts fall within the scope of protection of the present invention. The following will be described in detail in combination with the embodiments of the present invention.

[0021] Figure 1 、Figure 2 , Figure 3 is a schematic structural diagram of an embodiment of the present invention; a double helical planetary gear transmission reduction structure includes a sun gear 1, n P planet gears 2, a first internal gear ring 3, a second internal gear ring 4, a planetary gear carrier 5, a planetary gear mounting disc 6, a planetary gear pin shaft 7, a planetary gear bearing 8, a locking nut 9, a connecting bolt 10, a spline sleeve 11, a pressing plate 12, a spacer sleeve 13, a positioning bushing 14, and a screw 15. The sun gear 1 is connected to the internal spline shaft of the power input end through an external spline A to achieve the input of rotational speed and torque, and the floating connection of the sun gear is realized through the side clearance design of the external spline A. n P planet gears 2 are simultaneously meshed with the sun gear 1, the first internal gear ring 3, and the second internal gear ring 4 through double helical teeth to transmit the power input by the sun gear 1 to the planetary gears. The planetary gears 2 are connected to the planetary gear carrier 5 to transmit the power to the planetary gear carrier 5, and the planetary gear carrier 5 outputs the rotational speed and torque. The assembly between the sun gear 1 and the planetary gears 2 is carried out first. The sun gear 1 and the planetary gears 2 are positioned through a support tooling to ensure the correct meshing of the teeth of the sun gear 1 and the planetary gears 2. The connection between the planetary gear carrier 5 and the planetary gears 2 is realized through the planetary gear pin shaft 7 and the locking nut 9. A planetary gear mounting disc 6 is installed on the power input side of the planetary gears 2 close to the sun gear 1, and the planetary gear pin shaft 7 mounting holes corresponding to the planetary gear carrier 5 are provided on the planetary gear mounting disc 6. The planetary gear pin shaft 7 penetrates from the outside of the planetary gear mounting disc 6, passes through the planetary gear bearing 8, and is positioned in the corresponding inner hole of the planetary gear carrier 5. The extended end of the planetary gear pin shaft 7 is provided with an internal thread, and is tightened by the locking nut and pressed against between the planetary gear carrier 5 and the planetary gear mounting disc 6 to complete the fixation of the planetary gears 2. The internal gear ring adopts a split structure. After the sun gear 1 and the planetary gears 2 are fixedly installed, the first internal gear ring 3 and the second internal gear ring 4 are respectively installed from both end faces. The first internal gear ring 3 and the second internal gear ring 4 are fixed through connecting bolts and nuts. The outer sides of the first internal gear ring 3 and the second internal gear ring 4 are designed with spline structures and are connected to the spline sleeve 11, and the spline sleeve is connected to the casing to realize the floating design and overall fixation of the gear ring.

[0022] In a certain embodiment of the present invention, the machining accuracy of the tooth parts of the sun gear 1, the planetary gears 2, the first internal gear ring 3, and the second internal gear ring 4 should not be lower than grade 5 to ensure that the double helical planetary gear train obtains good load sharing performance.

[0023] In a certain embodiment of the present invention, the external spline A on the sun gear 1 is specifically an involute barrel-shaped spline, and the barrel-shaped amount is obtained through simulation analysis to ensure that good contact imprints are finally obtained on the teeth of the sun gear and the spline of the input end, improve the stress levels of the gear tooth surfaces and the spline tooth surfaces, and ensure smooth transmission.

[0024] In a certain embodiment of the present invention, the number of assembled planet gears 2, denoted as n P is not less than 3. For the inner hole to install the planet gear bearing 8, a rolling bearing structure is required, and this bearing needs to have a certain self-aligning ability to adjust the axis deflection of the planet gear 2 caused by errors and loads during operation. Between n P planet gears 2, before assembly, the tooth thickness difference of the herringbone gear teeth needs to be controlled within 0.012 mm.

[0025] In a certain embodiment of the present invention, the planet gear carrier 5 and the planet gear mounting disc 6 need to be processed by a combined machining method for the machining of n P mounting holes to ensure the position accuracy of the mating holes with the planet gear pin 7. As shown in Figure 2 . For the combined machining method shown, taking the planet gear carrier 5 as the machining reference, on the planet gear carrier 5, set positioning holes with the same number as n P mounting holes, evenly distributed between n P mounting holes. After the mounting holes and positioning holes on the planet gear carrier 5 are machined, use n P positioning bushings 14 and n P screws 15 to connect the spacer sleeve 13. Use a combined drilling method to machine the positioning holes φC of the planet gear mounting disc 6 and n P spacer sleeves 13. After machining, install n P positioning bushings 14 and n P screws 15 to achieve precise positioning between the planet gear carrier 5 and the planet gear mounting disc 6. Then, taking φA on the planet gear carrier 5 as the reference, machine the mounting hole φB on the planet gear mounting disc 6 to complete the combined machining between the planet gear carrier 5, the planet gear mounting disc 6 and the planet gear pin 7.

[0026] In a certain embodiment of the present invention, the first internal gear ring 3 and the second internal gear ring 4 are of single helical tooth structure and need to be combined into a herringbone gear ring through connecting bolts 10. During machining, after the first internal gear ring 3 and the second internal gear ring 4 are each rough machined, they are assembled. As shown in Figure 3 , positioning is achieved through positioning spigots. The positioning spigots are designed as a small-size transition fit. Combined machining is used to complete the grinding of the helical tooth surface, the machining of the spline and the bolt connection holes to ensure the installation and positioning accuracy and achieve good alignment of the teeth on both sides of the herringbone gear.

[0027] In a certain embodiment of the present invention, short spline B structures are designed on the outer sides of the first internal gear ring 3 and the second internal gear ring 4 at positions symmetric to the center of the herringbone teeth. The stress state of the spline B tooth surface is determined through simulation analysis, and the requirements for tooth direction and tooth profile modification are given to ensure that edge contact does not occur during the meshing process of the spline pair. By dynamically analyzing the deformation of the spline B of the first internal gear ring 3 and the second internal gear ring 4 under the working load condition, the side clearance of the spline pair is reserved according to the deformation amount, providing necessary off-axis load adjustment space for the gear ring. The surface of the spline pair adopts a surface strengthening process to improve the wear resistance of the spline pair.

[0028] In a certain embodiment of the present invention, the spline sleeve 11 is provided with a long spline C structure and meshes with the short spline B of the first internal gear ring 3 and the second internal gear ring 4 simultaneously. The spline sleeve 11 is connected to the reducer housing body, and the connection method adopts general connection forms such as bolts and pre-set studs. A limiting edge is designed on the outer side end surface of the spline sleeve 11 and the first internal gear ring 3, and a clearance structure is designed between the edge and the end surface of the first internal gear ring 3, with the clearance not less than 0.8 mm. A wear-resistant coating is applied to the surface of the spline sleeve 11 close to the first internal gear ring 3. After coating, the clearance value between the edge and the end surface of the internal gear ring can be appropriately reduced, taking advantage of the wear-resistant performance of the coating.

[0029] In a certain embodiment of the present invention, the pressure plate 12 is installed on the outer side end surface of the second internal gear ring 4, with a clearance not greater than 0.8 mm from it, and a wear-resistant coating is applied to the surface of the pressure plate 12 close to the second internal gear ring 4. The function of the pressure plate 12 is the same as that of the edge of the spline sleeve 11.

[0030] The power input end of the sun gear 1 is designed as an external spline A connection structure, which can realize the floating of the sun gear. By modifying the spline teeth, the equal load adjustment ability of the herringbone tooth planetary gear train is improved.

[0031] The split design of the planetary gear carrier 5, the planetary gear pin shaft 7, and the planetary gear mounting disc 6 can realize the assemblability of the herringbone tooth sun gear 1 and the planetary gear 2.

[0032] The internal gear ring is designed as a split structure, and the herringbone teeth of the internal gear ring and the herringbone teeth of the planetary gear can be meshed from both ends, enabling the gear ring and the planetary gear to have assemblability.

[0033] A spline structure is designed on the outer side of the internal gear ring and is connected to the spline sleeve fixed on the reducer housing, realizing the fixation of the internal gear ring while providing a certain space for the floating of the internal gear ring. At the same time, the floating characteristics of the gear ring can be improved through the design of the spline tooth profile, tooth clearance, and tooth width.

[0034] A trapezoidal stop and bolt connection holes are designed between the two half internal gear rings for positioning and connecting and fixing the two half gear rings, realizing an integrated structural form after the gear ring is installed and providing working stability.

[0035] When the two half internal gear rings are processed, they are assembled and installed after their respective rough machining. The combined machining method is adopted to complete the gear grinding of the herringbone teeth on both sides, the forming of the spline teeth, and the machining of the bolt connection holes, which can ensure the installation and positioning accuracy and achieve good centering of the herringbone teeth on both sides.

[0036] The inner holes of the planetary gear mounting disc and the planetary gear carrier that cooperate with the planetary gear pin shafts are machined by the combined machining method, and spacer sleeves, positioning bushings and screws for positioning and connecting functions are designed on the circumference, which is convenient for accurate positioning during machining, realizes good machining performance, and ensures high positioning accuracy after the planetary gears are installed.

[0037] The above herringbone tooth planetary transmission reduction structure realizes the double floating of the sun gear 1, the first internal gear ring 3 and the second internal gear ring 4 through configuration design, assembly design, combined machining design, etc., ensures good assemblability of the herringbone tooth planetary transmission, can obtain good load sharing characteristics, and meets the use requirements.

[0038] In addition, unless otherwise defined, the technical terms or scientific terms used in the description of this application should be the ordinary meanings understood by those of ordinary skill in the art to which this application belongs. The words indicating directions such as "upper", "lower", "left", "right", "center", "vertical", "horizontal", "inner", "outer", etc. used in the description of this application are only used to indicate relative directions or position relationships, rather than implying that the device or element must have a specific orientation, be constructed and operated in a specific orientation. When the absolute position of the object being described changes, its relative position relationship may also change accordingly. Therefore, it cannot be understood as a limitation to this application. The terms "first", "second", "third" and similar terms used in the description of this application are only for descriptive purposes to distinguish different components, and cannot be understood as indicating or implying relative importance. The similar words such as "a", "one" or "the" used in the description of this application should not be understood as an absolute limitation on the quantity, but should be understood as having at least one. The similar words such as "including" or "comprising" used in the description of this application are intended to mean that the elements or objects appearing before this word cover the elements or objects listed after this word and their equivalents, without excluding other elements or objects.

[0039] In addition, it should be noted that, unless otherwise clearly specified and limited, the similar words such as "installed", "connected" and "connected" used in the description of this application should be understood in a broad sense. For example, the connection can be a fixed connection, a detachable connection, or an integral connection; it can be a mechanical connection or an electrical connection; it can be directly connected or indirectly connected through an intermediate medium, and it can also be the communication inside two elements. Those skilled in the art can understand its specific meaning in this application according to the specific situation.

[0040] The above are only specific embodiments of the present invention and are not intended to limit the present invention. Any person skilled in the art may, within the spirit and principles of the present invention, use the disclosed technical content to make changes or modifications to equivalent embodiments with equivalent changes and apply them to other fields. However, any simple modifications, equivalent changes and modifications made to the above embodiments based on the technical essence of the present invention without departing from the technical solution content of the present invention, any modifications, equivalent substitutions, improvements, etc., shall be included within the protection scope of the present invention.

Claims

1. A double helical planetary gear transmission reduction structure, characterized in that, including a sun gear, n P planet gears, a first internal gear ring, a second internal gear ring, a planet gear carrier, a planet gear mounting disc, planet gear pin shafts, planet gear bearings, lock nuts, connecting bolts, spline sleeves, pressing plates, spacer sleeves, and positioning bushings; the sun gear is connected to the internal spline shaft of the power input end through an external spline A, and a floating design of the sun gear is achieved by reserving a side clearance of the spline pair; the sun gear and the planet gears are meshed and connected through herringbone teeth; the planet gears and the planet gear carrier are locked and connected through the planet gear pin shafts and the lock nuts to transmit the power of the planet gears to the planet gear carrier; The supporting tooling positions the sun gear, installs the planetary gear bearings into the inner holes of the planetary gears, and installs n P planetary gears respectively along the radial direction of the sun gear to mesh the herringbone teeth and fix their positions; a planetary gear mounting disc is placed on the power input side of the planetary gear close to the sun gear, and the planetary gear mounting disc is provided with mounting holes consistent with the number n P of the planetary gears. The corresponding number of planetary gear pins equal to the number n P of the planetary gears respectively pass through the planetary gear mounting disc and the inner holes of the planetary gear bearings from the power input side of the sun gear, and are correspondingly installed into the n P mounting holes provided on the planetary gear carrier; threads are provided at the inner hole positions of the mating shaft sections of the planetary gear pins and the planetary gear carrier, and the lock nuts are locked to the internal threads of the planetary gear pins.

2. The structure according to claim 1, characterized in that, The internal gear ring meshing with the herringbone teeth of the planetary gear is designed as a split-structured first internal gear ring and a second internal gear ring. After the sun gear and the planetary gears are fixedly installed, the first internal gear ring and the second internal gear ring are respectively inserted from both end faces of the planetary gears. After the first internal gear ring and the second internal gear ring are assembled and abutted, they are fixed into one body by connecting bolts to form a herringbone gear ring. Spline B is designed on the outer sides of the first internal gear ring and the second internal gear ring to realize the floating connection of the herringbone gear ring. The first internal gear ring and the second internal gear ring are simultaneously connected to the spline sleeve through their respective spline Bs. One end of the spline sleeve is designed with a stop structure for limiting, and the other end is installed with a pressing plate for limiting. The spline sleeve and the pressing plate are both connected to the casing to realize the relative fixation of the internal gear ring. The machining accuracy of the tooth parts of the sun gear, the planetary gears, the first internal gear ring, and the second internal gear ring should not be lower than grade 5.

3. The structure according to claim 1, wherein The external spline A on the sun gear is specifically an involute drum spline, and the drum amount is obtained through simulation analysis.

4. The structure according to claim 1, wherein The assembled quantity n of the planetary gears P shall be no less than 3, and a rolling bearing structure shall be selected for installing the planetary gear bearings in the inner holes.

5. The structure according to claim 1, characterized in that, The described planet gear carrier and planet gear mounting disc need to be processed by a combined machining method for the machining of n P mounting holes to ensure the positional accuracy of the mating holes with the planet gear pin shafts; the described combined machining method takes the planet gear carrier as the machining reference, and sets n P locating holes with the same number as the n P mounting holes, evenly distributed between the n P mounting holes. After the mounting holes and locating holes on the planet gear carrier are machined, n P locating bushings and n P screw connection spacer sleeves are used to machine the locating holes φC of the planet gear mounting disc and the n P locating bushings and n P screws are installed after machining to achieve precise positioning between the planet gear carrier and the planet gear mounting disc; then, with φA on the planet gear carrier as the reference, the mounting hole φB on the planet gear mounting disc is machined to complete the combined machining between the planet gear carrier, the planet gear mounting disc and the planet gear pin shaft.

6. The structure according to claim 1, characterized in that, The first internal gear ring and the second internal gear ring are of single helical tooth structure and need to be combined by connecting bolts to form a herringbone gear ring. During machining, after the first internal gear ring and the second internal gear ring are respectively rough machined, they are installed and combined, and positioning is realized through positioning stop mouths. The positioning stop mouths are designed with a small-size transition fit, and combined machining is used to complete the grinding of the helical tooth surface, the machining of the spline and the bolt connection holes.

7. The structure according to claim 1, wherein Short spline B structures are designed on the outer sides of the first internal gear ring and the second internal gear ring at positions symmetrical to the center of the herringbone teeth. The stress state of the spline B tooth surface is determined through simulation analysis, and the requirements for tooth direction and tooth profile modification are given to ensure that there will be no edge contact during the meshing process of the spline pair.

8. The structure according to claim 1, wherein The spline sleeve is provided with a long spline C structure and meshes with the short spline B of the first internal gear ring and the second internal gear ring at the same time. The spline sleeve is connected to the main body of the reducer casing, and the connection method adopts the form of bolt and pre-set stud connection. A limiting stop edge is designed on the outer end face side of the spline sleeve and the first internal gear ring. The space between the stop edge and the end face of the first internal gear ring is designed as a clearance structure, and the clearance is not less than 0.8 mm. A wear-resistant coating is applied to the surface of the spline sleeve 11 close to the first internal gear ring 3.

9. The structure according to claim 1, wherein The pressing plate is installed on the outer end face of the second internal gear ring, and the clearance between them is not more than 0.8 mm. A wear-resistant coating is applied to the surface of the pressing plate close to the second internal gear ring. The function of the pressing plate is the same as that of the stop edge of the spline sleeve.

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