CN112032260B

CN112032260B - Method for assembling and phase adjusting equidirectional output structure

Info

Publication number: CN112032260B
Application number: CN202010855936.8A
Authority: CN
Inventors: 邵广军; 张坤; 许建忠; 康少博; 张�浩; 董进朝; 乔永钦; 崔云翔; 许俊伟; 邢鹤琛
Original assignee: Zhengzhou Research Institute of Mechanical Engineering Co Ltd
Current assignee: Zhengzhou Research Institute of Mechanical Engineering Co Ltd
Priority date: 2020-08-24
Filing date: 2020-08-24
Publication date: 2021-08-17
Anticipated expiration: 2040-08-24
Also published as: CN112032260A

Abstract

The invention relates to the technical field of double-screw extruder gear boxes, and discloses an assembling and phase adjusting method of a homodromous output structure, which comprises a box body, a first output shaft system, a middle shaft system and a second output shaft system, wherein the method comprises the following steps: s1, measuring the angle error between the transmission parts in each shafting; s2, assembling each shafting and transmission parts on the box body according to the design position; s3, calculating the actual phase deviation; s4, calculating the number of teeth and the axial movement required to adjust the rotation; s5, adjusting according to the calculation result in S4. The method for adjusting the output phase does not need to modify the internal structure of the existing gear box, ensures the torque transmission capacity of the gear pair, can adjust according to the result obtained by accurate measurement and calculation, does not need to be repeatedly disassembled and assembled, can greatly reduce the adjustment difficulty, shortens the assembly and adjustment time, and greatly saves manpower and material resources.

Description

Method for assembling and phase adjusting equidirectional output structure

Technical Field

The invention relates to the technical field of gear boxes of double-screw extruders, in particular to an assembling and phase adjusting method of a equidirectional output structure.

Background

The twin-screw extruder is developed on the basis of a single-screw extruder, has the characteristics of good feeding property, mixing plasticity, air exhaust property, extrusion stability and the like, and is widely applied to molding processing of extruded products. The twin-screw extruder includes a co-rotating twin-screw extruder and a counter-rotating twin-screw extruder as viewed in the rotation direction of the twin-screws. The co-rotating twin-screw extruder is also called as an engaged co-rotating parallel twin-screw extruder, has the advantages of high conveying efficiency, strong dispersive mixing capability, good self-cleaning performance, uniform residence time distribution of materials in the extruder, good adaptability and the like, is widely applied to blending modification among different plastics, blending modification among plastics and rubber, blending modification of various additives and plastics and the like, and is the first choice of polymer modification continuous mixing equipment.

The core of the co-rotating twin-screw extruder is to perform main mixing operation by two screws arranged in parallel, the two screws are generally driven by a motor, and power transmission, torque distribution and the like are realized between the motor and the two screws by a gear box. The gear box of the co-rotating twin-screw extruder is provided with two output shafts for connection with the two screws mentioned above, so that the two output shafts must have the same rotational speed and rotational direction. And two screws in the co-rotating twin-screw extruder need strict in-phase requirements, and two output shafts of a gear box of the co-rotating twin-screw extruder are usually connected with the two screws by adopting a spline structure, so that the output phases of the two output shafts of the gear box need to be the same. In the prior art, assembly is usually carried out by adopting an trial and error method, namely, the tooth positions meshed with each other between the gears are continuously adjusted during assembly, each gear shaft system or each gear and the like need to be repeatedly disassembled and reassembled, time and labor are wasted, and sometimes the gear shaft system or the gears cannot be adjusted to the positions in the same phase even if one or two days are spent.

In order to make the in-phase adjustment of the output shaft of the gearbox simpler, some solutions in the prior art are implemented by changing the internal structure of the gearbox. For example, the chinese utility model patent is named as the in-phase adjusting device of the output shaft spline of the twin-screw extruder (application No. 201120501565. X), the gear box for the parallel twin-screw extruder (application No. 201420274149.4), the in-phase adjusting device of the output shaft spline of the twin-screw extruder (application No. 201821243552.5), and the like. The technical scheme in these patents is through setting up adjustable gear to through rising tight cover or nut come locking adjustable gear, or change the idler shaft between two output shafts into two integral key shafts of splined connection, thereby improve the convenience of gear box looks adjustment. However, these structures add more connections or fits, making the internal structure of the gearbox more complex and more expensive, and they tend to reduce torque transmission capability and are generally not suitable for use in high speed applications. And even though these structures improve the convenience of the same phase adjustment of the gearbox to a certain extent, the same phase precision after adjustment is not ideal.

In addition, in actual gear transmission, a backlash inevitably exists between a pair of meshed gears, and the structure in the prior art cannot basically reduce or eliminate phase deviation caused by the backlash.

Disclosure of Invention

The invention provides an assembling and phase adjusting method of a homodromous output structure to overcome the defects in the prior art.

The invention achieves the above object by the following technical solutions.

The assembly and phase adjustment method of the same-direction output structure comprises a box body, a first output shaft system, an intermediate shaft system and a second output shaft system, wherein the first output shaft system comprises a first output shaft rotationally connected to the box body and a gear A fixed on the first output shaft, the intermediate shaft system comprises an idler shaft rotationally connected to the box body, a gear B and a gear C fixed on the idler shaft, the second output shaft system comprises a second output shaft rotationally connected to the box body and a gear D fixed on the second output shaft, the gear A and the gear B are externally meshed, the gear C and the gear D are helical gears which are externally meshed with each other, the torque transmission direction is that the first output shaft system transmits torque to the intermediate shaft system, and the intermediate shaft system transmits the torque to the intermediate shaft system in the torque transmission directionThe gear A is transmitted to a second output shaft system, the axes of a first output shaft and a second output shaft are parallel, the output direction is the same, the output rotating speed is also the same, an external spline E is arranged at the output end of the first output shaft, an external spline F is arranged at the output end of the second output shaft, the shapes of the external spline E and the external spline F are the same, the design positions of the end face of the external spline E of the first output shaft and the end face of the external spline F of the second output shaft are in the same plane, the design positions of the external spline E and the external spline F are in the same phase, the number of teeth of the gear A is recorded as Z_AThe number of teeth of gear B is denoted as Z_BNumber of teeth of gear C is denoted as Z_CThe number of teeth of gear D is noted as Z_DAnd the number of teeth of the external spline F is represented as Z_F，Z_DAnd Z_FNot equal, the method comprises:

determining that the rotation directions of all the gears, the external splines and the shaft are consistent with a reference direction of clockwise or anticlockwise, wherein parameters related to the rotation directions in the method are specified to be positive values clockwise or specified to be positive values anticlockwise;

step S1, measuring the angle error of the external spline E and the gear A in the assembled first output shaft system, and recording the angle error as phi on the basis of the external spline E_A(ii) a Measuring the angle error of the gear B and the gear C in the assembled middle shaft system, and recording the angle error as phi by taking the gear B as the reference_C(ii) a Measuring the angle error of the gear D and the external spline F in the assembled second output shaft system, and recording the angle error as phi by taking the gear D as the reference_F；

Step S2, assembling the shafting on the box body, wherein the external spline E and the external spline F are assembled according to the design position, and the end surface of the external spline E of the first output shaft and the end surface of the external spline F of the second output shaft are in the same plane;

step S3, calculating the angle error phi of the external spline E and the gear A_AThe angular deviation resulting from gear B is noted as θ_B，θ_B=-φ_A*（Z_A/Z_B) (ii) a The total angular deviation of gear C is calculated and recorded as θ_C，θ_C=θ_B+φ_C(ii) a Calculating the total angular deviation theta due to the gear C_CResulting in the angular deviation of the gear D and recordingIs theta_D，θ_D=-θ_C*（Z_C/Z_D) (ii) a The total angular deviation of the male spline F is calculated and recorded as θ_F，θ_F=θ_D+φ_F(ii) a The direction of the external spline F needing to be adjusted and rotated is opposite to the direction of the total angular deviation of the external spline F, and the angle of the external spline F needing to be adjusted and rotated is recorded as gamma_{Regulating device}Then γ_{Regulating device}=-θ_FCalculating the phase shift of the external spline F caused by each tooth position of the gear D and recording the phase shift as delta_DF，Δ_DF=360/Z_D-360/Z_F；

Step S4, using gamma_{Regulating device}Divided by Δ_DFThe obtained integer quotient is the number of teeth of the gear D which need to be adjusted and rotated and is recorded as n, and the obtained remainder is the residual adjustment rotation angle and is recorded as gamma_SurplusAnd hold γ_SurplusAnd gamma_{Regulating device}Positive and negative are the same, calculate gamma_SurplusThe lead section length of the gear D corresponding to the absolute value of (A) is the axial movement amount of the second output shaft and is recorded as L_SurplusThe gear D is inevitably rotated when moving axially, and the rotation direction and the residual adjustment rotation angle gamma_SurplusThe corresponding rotating directions are the same;

step S5, the gear D is adjusted and rotated by n tooth positions while keeping the phase position of the external spline E unchanged, and then the gear D is moved by the axial movement amount L_SurplusAxially moving the second output shaft, and ensuring the rotation direction of the gear D and the residual adjustment rotation angle gamma when axially moving the second output shaft_SurplusThe corresponding rotation directions are the same.

The case in this embodiment usually includes other shafting and gears, such as the input shaft and the gear thereon, but the purpose of this embodiment is to relate to the structures of the rotating shaft, the gear, the spline, and the like in the first output shafting, the intermediate shafting, and the second output shafting, so the structure of other shafting and the like is not described in the claims, and those skilled in the art can design and implement the present invention with reference to the prior art.

In the method, it is determined that the rotation directions of all the gears, the external splines and the shafts are consistent with a reference direction of clockwise or counterclockwise, for example, the direction from the external spline E to the gear a of the axis of the first output shaft may be used as the reference direction, and in this reference direction, if the rotation direction of the external spline E is clockwise, the rotation direction of the gear a is clockwise, the rotation directions of the gear B and the gear C are counterclockwise, and the rotation directions of the gear D and the external spline F are clockwise.

In the method, the parameter related to the rotation direction is defined to be a positive value clockwise or a positive value anticlockwise. For example, if the parameter related to the rotation direction is specified to be positive counterclockwise and negative clockwise, the angular errors of the external spline E and the gear a in the assembled first output shaft system are measured, and with reference to the external spline E, that is, if the external spline E is fixed and the error of the gear a relative to the external spline E is 0.35 degrees counterclockwise, phi is measured_A=0.35 degrees, if the error of the gear a relative to the external spline E is 0.35 degrees clockwise, phi_A=0.35 degrees; measuring the angle error of the gear B and the gear C in the assembled middle shafting, and taking the gear B as the reference, namely if the gear B is fixed and the error of the gear C relative to the gear B is 0.2 degrees in a counterclockwise way, phi_C=0.2 degrees, if the error of the gear C with respect to the gear B is 0.2 degrees clockwise, phi_C=0.2 degrees; measuring the angle error of the gear D and the external spline F in the assembled second output shaft system, and taking the gear D as a reference, namely if the gear D is fixed and the error of the external spline F relative to the gear D is 0.15 degrees in a counterclockwise way, phi is measured_F=0.15 degrees, if the error of the external spline F with respect to the gear D is 0.15 degrees clockwise, phi_F=0.15 degrees; similarly, if the calculated angle error phi is smaller than the calculated angle error phi_AResulting in the angular deviation theta of the gear B_B=0.18, the angular deviation of the gear B is described as being counterclockwise, if the calculated angular error phi is due to_AResulting in the angular deviation theta of the gear B_B=0.18, the angular deviation of the gear B is indicated as clockwise, and the other rotation-direction-related parameters follow the same rule, which is not listed here.

In step S1 of the method, the angular errors between the gears and the external splines in the first output shaft system, the intermediate shaft system and the second output shaft system that are assembled can be measured by using a three-coordinate measuring machine.

In step S2 of the method, it is required that the external spline E and the external spline F are assembled according to a designed position, and the designed positions of the external spline E and the external spline F are in the same phase, but actually, due to various machining and assembling errors, there is a phase deviation between the external spline E and the external spline F, so that the assembly of the external spline E and the external spline F according to the designed same phase is allowed to have a phase deviation, and it is determined whether to assemble according to the designed same phase.

The total angular deviation theta of the external spline F calculated in the method_FI.e. the actual phase deviation of the external splines E and F. The method for adjusting the positions of the external splines E and the external splines F to the same phase is realized by adjusting the rotating gear D and axially moving the second output shaft, and after the second output shaft is axially moved, the end face of the external spline E of the first output shaft and the end face of the external spline F of the second output shaft are inevitably axially dislocated, but the axial dislocation is small, and when a screw is connected, the axial dislocation is increased between the end face of the external spline E and the end face of the screw, or between the end face of the external spline F and the end face of the screw, and the axial movement L is increased_SurplusThe same thickness of the gap piece. The phase deviation between the external spline E and the external spline F is generally caused by machining and assembling errors, and the axial movement of the gear D is basically small when the same phase is adjusted according to the method, so that the change of the meshing contact area between the gear D and the gear C is small, and the influence on the meshing effect between the gears and the torque transmission capacity of a gear pair is small. More importantly, the same phase is adjusted according to the method without modifying the internal structure of the existing gear box, more connection or matching relation is not needed, the material and process cost is not improved, the torque transmission capacity of the gear pair is ensured, the low-speed and high-speed extruders are suitable for use, in addition, the results obtained through accurate measurement and calculation are adjusted according to the obtained results, and therefore, gear shafting or gears and the like are not needed to be adjustedThe disassembly and the assembly are repeated, the adjustment difficulty can be reduced, the assembly and adjustment time is shortened, and the manpower and the material resources are greatly saved.

As an optimized method, the step S2 includes a step S21, which measures the circumferential backlash between the gear A and the gear B and is marked as j_ABThe backlash angle at which the gear B needs to rotate when the gear A cancels the tooth profile single-sided circumferential backlash based on the operating state is represented as μ_BThen μ_B=+/-（j_AB/dp_B) (180/pi); measuring the circumferential backlash between gear C and gear D and recording j_CDThe backlash angle at which the gear D needs to rotate when the gear C is offset with respect to the gear C based on the operating state and the tooth profile single-sided circumferential backlash is expressed as μ_DThen μ_D=+/-（j_CD/dp_D) (180/pi); wherein dp_BIs the pitch diameter, dp, of gear B_DIs the pitch diameter of the gear D, the backlash angle mu_BAnd the backlash angle mu_DIs determined according to the method of claim 1;

the step S3 is: calculating the angular error phi due to the external spline E and the gear A_AThe angular deviation resulting from gear B is noted as θ_B，θ_B=-φ_A*（Z_A/Z_B) (ii) a The total angular deviation of gear C is calculated and recorded as θ_C，θ_C=θ_B+μ_B+φ_C(ii) a Calculating the total angular deviation theta due to the gear C_CThe angular deviation caused by the gear D is noted as theta_D，θ_D=-θ_C*（Z_C/Z_D) (ii) a The total angular deviation of the male spline F is calculated and recorded as θ_F，θ_F=θ_D+μ_D+φ_F(ii) a The direction of the external spline F needing to be adjusted and rotated is opposite to the direction of the total angular deviation of the external spline F, and the angle of the external spline F needing to be adjusted and rotated is recorded as gamma_{Regulating device}Then γ_{Regulating device}=-θ_FCalculating the phase shift of the external spline F caused by each tooth position of the gear D and recording the phase shift as delta_DF，Δ_DF=360/Z_D-360/Z_F。

If the backlash is not calculated in advance, the external spline E and the external spline F can be in the same phase state in a static state after the same phase adjustment, but after the equipment runs, a certain phase deviation exists between the external spline E and the external spline F. The optimized method takes the backlash into account in advance, i.e. adjusts it based on the operating conditions, thus ensuring that the same phase of the output is more accurate under operating conditions. In actual operation, oil films exist between the meshed tooth surfaces, and although the oil films have certain thicknesses, the oil films have very small thicknesses, so that the influence on the phase is very small and can be ignored.

Compared with the prior art, the invention mainly has the following beneficial effects: the method for adjusting the same phase does not need to reform the internal structure of the existing gear box, does not need to increase more connection or matching relation, does not improve material and process cost, ensures the torque transmission capability of a gear pair, is applicable to both low-speed and high-speed extruders, and can adjust the same phase according to the obtained result because of the result obtained by accurate measurement and calculation, so that the repeated disassembly and reassembly of various gear shafting or gears and the like is not needed, the adjustment difficulty is greatly reduced, the assembly and adjustment time is shortened, and manpower and material resources are greatly saved.

Drawings

Fig. 1 is a schematic view of an internal structure of a gearbox according to a first embodiment of the present invention.

Fig. 2 is a schematic diagram of the same phase positions of the gears and the external splines at the two output shafts and the idler shaft in a designed state without angular error according to the first embodiment of the present invention.

FIG. 3 is a schematic diagram showing the relative positions of the helical gear A and the external spline E in the first embodiment of the present invention.

Fig. 4 is a partial schematic view of actually measured relative positions of a helical gear a and an external spline E in the first embodiment of the present invention.

FIG. 5 is a schematic diagram of the relative positions of the bevel gears B and C according to the first embodiment of the present invention.

Fig. 6 is a partial schematic view of the actually measured relative positions of the bevel gears B and C according to the first embodiment of the present invention.

FIG. 7 is a schematic diagram showing the relative positions of the helical gear D and the external spline F in the first embodiment of the present invention.

Fig. 8 is a partial schematic view of actually measured relative positions of a helical gear D and an external spline F in the first embodiment of the present invention.

Fig. 9 is a schematic position diagram of the two output shafts and the gears and the external splines at the idler shaft in the same phase according to the design under the condition of angular error.

Fig. 10 is a schematic diagram illustrating a phase change of the external spline F when the helical gear D rotates counterclockwise by one tooth position in the first embodiment of the present invention.

FIG. 11 is a partial schematic view of a bevel gear A and a bevel gear B in a state where backlash exists in a second embodiment of the present invention, that is, a partial enlarged view of a bevel gear A and a bevel gear B in a state where backlash exists at P in FIG. 9.

FIG. 12 is a partial schematic view of a bevel gear C and a bevel gear D in a state where backlash exists in a second embodiment of the present invention, that is, a partial enlarged view of a bevel gear C and a bevel gear D in a state where backlash exists at Q in FIG. 9.

Fig. 13 is a schematic view of the internal structure of a gearbox according to a third embodiment of the present invention.

Fig. 14 is a schematic diagram of the same phase positions of the gears and the external splines at the two output shafts and the idler shaft in the designed state without angular error according to the third embodiment of the present invention.

FIG. 15 is a schematic diagram showing the relative positions of helical gears A and external splines E in the third embodiment of the present invention.

Fig. 16 is a partial schematic view showing the actually measured relative positions of the helical gear a and the external spline E in the third embodiment of the present invention.

FIG. 17 is a schematic diagram of the relative positions of bevel gears B and bevel gears C in the third embodiment of the present invention.

Fig. 18 is a partial schematic view showing the relative positions of the bevel gears B and C actually measured in the third embodiment of the present invention.

FIG. 19 is a schematic view of the relative positions of the helical gear D and the external spline F design in the third embodiment of the present invention.

Fig. 20 is a partial schematic view showing the actually measured relative positions of the helical gear D and the external spline F in the third embodiment of the present invention.

Fig. 21 is a schematic position diagram of the two output shafts and the gears and the external splines at the idler shaft according to the third embodiment of the present invention in the state of angular error after being assembled in phase according to the design.

FIG. 22 is a partial schematic view of a third embodiment of the present invention, showing a bevel gear A and a bevel gear B in the state of backlash, that is, an enlarged partial view of the bevel gear A and the bevel gear B in the state of backlash at X in FIG. 21.

FIG. 23 is a partial schematic view of a third embodiment of the present invention, showing a bevel gear C and a bevel gear D in the state of backlash, that is, an enlarged partial view of a bevel gear C and a bevel gear D in the state of backlash at Y in FIG. 21.

Fig. 24 is a schematic diagram showing a phase change of the external spline F when the helical gear D rotates counterclockwise by one tooth position in the third embodiment of the present invention.

Detailed Description

The invention is further described below with reference to the accompanying drawings. The drawings are for illustrative purposes only and are not to be construed as limiting the patent.

In order to explain the embodiment more simply, some parts which are known to those skilled in the art in the drawings or description but are not relevant to the main content of the present invention will be omitted. In addition, some components in the drawings may be omitted, enlarged or reduced for convenience of description, but do not represent the size or the entire structure of an actual product.

The first embodiment is as follows:

as shown in fig. 1, the gear box of the twin-screw extruder in the prior art is schematically configured, and the gear box includes a box body 1 (only a part of the box body 1 is shown in the figure, and a person skilled in the art can design and implement the gear box in the prior art), an input shaft system 2, a secondary speed reduction shaft system 3, a first output shaft system 4, an intermediate shaft system 5, and a second output shaft system 6.

The input shaft system 2 includes an input shaft 21 rotatably connected to the casing 1 and a helical gear H22 fixed to the input shaft 21. The left end of the input shaft 21 in fig. 1 is exposed to the left side of the case 1 for connection with an external motor. The secondary speed reducing shafting 3 comprises a secondary rotating shaft 31 rotatably connected to the box body 1, and a bevel gear K32 and a bevel gear M33 which are fixed on the secondary rotating shaft 31. The first output shaft system 4 includes a long output shaft 41 rotatably connected to the case 1 and a helical gear N42 and a helical gear a43 fixed to the long output shaft 41. The middle shafting 5 comprises an idler shaft 51 rotationally connected to the box body 1, and a bevel gear B52 and a right-hand bevel gear C53 which are fixed on the idler shaft 51. The second output shafting 6 includes a short output shaft 61 rotatably connected to the casing 1 and a left helical gear D62 fixed to the short output shaft 61. The axes of the input shaft 21, the secondary rotating shaft 31, the long output shaft 41, the idler shaft 51 and the short output shaft 61 are parallel to each other, a bevel gear H22 is externally meshed with a bevel gear K32, a bevel gear M33 is externally meshed with a bevel gear N42, a bevel gear A43 is externally meshed with a bevel gear B52, and a bevel gear C53 is externally meshed with a bevel gear D62. The long output shaft 41 and the short output shaft 61 have the same output direction and the same output rotation speed. The output end of the long output shaft 41 is provided with an integrally formed external spline E44, and the output end of the short output shaft 61 is provided with an integrally formed external spline F63. The external spline E44 and the external spline F63 are the same in shape, and both the external spline E44 and the external spline F63 are exposed on the right side of the box body 1 as shown in FIG. 1 and are used for spline connection of two screws of a double-screw extruder.

The torque transmission direction in the gearbox is that the input shaft 21 is transmitted to the secondary rotating shaft 31, the secondary rotating shaft 31 is transmitted to the long output shaft 41, the long output shaft 41 is transmitted to the idler shaft 51, and the idler shaft 51 is transmitted to the short output shaft 61. As shown in fig. 1, the design positions of the end surface of the male spline E44 and the end surface of the male spline F63 are in the same plane. As shown in fig. 2, the phase design positions of the external spline E44 and the external spline F63 are in phase. For the sake of easy understanding, the short output shaft 61 and the bevel gear D62 and the external spline F63 thereon are shown in fig. 2 rotated at an angle relative to the bevel gear B52, without changing the actual structure and having any influence on the method of the present invention. The same phase design positions of the external spline E44 and the external spline F63 shown in fig. 2 are: the line of symmetry of the keyway of helical gear a43, the line of symmetry of a tooth profile of helical gear a43 and the line of symmetry of a tooth profile of the male spline E44 are coincident and in a vertical position, and the keyway of helical gear a43, the tooth profile of helical gear a43 and the tooth profile of the male spline E44 are all above the axial center of the male spline E44; the line of symmetry of the keyway of helical gear D62, the line of symmetry of a tooth profile of helical gear D62 and the line of symmetry of a tooth profile of the male spline F63 are coincident and in a vertical position, and the keyway of helical gear D62, the tooth profile of helical gear D62 and the tooth profile of the male spline F63 are all above the axial center of the male spline F63.

The center-to-center distance between the long output shaft 41 and the idler shaft 51 is equal to the sum of the pitch circle radius of bevel gear a43 and the pitch circle radius of bevel gear B52, i.e., the center-to-center distance between bevel gear a43 and bevel gear B52 is the standard center-to-center distance. The center distance between the idler shaft 51 and the short output shaft 61 is equal to the sum of the pitch circle radius of the bevel gear C53 and the pitch circle radius of the bevel gear D62, that is, the center distance between the bevel gear C53 and the bevel gear D62 is the standard center distance.

In the embodiment, relevant parameters such as gears, external splines, gear engagement and the like in the gearbox are listed one by one for subsequent calculation. Helical gear A43 has Z teeth_A，Z_A= 29. The number of teeth of helical gear B52 is denoted as Z_B，Z_B= 55. The number of teeth of helical gear C53 is denoted as Z_C，Z_C= 55. The number of teeth of helical gear D62 is denoted as Z_D，Z_D= 29. The pitch circle diameter of helical gear D62 when helical gear C53 meshes with helical gear D62 is denoted as dp_D，dp_D=232 mm. The helix angle of helical gear D62 is denoted as β_D，β_D=20 degrees. The number of teeth of the external spline E44 is Z_EThe number of teeth of the external spline F63 is denoted as Z_F，Z_E=Z_F=28。

The method for assembling and phase adjusting the equidirectional output structure comprises the following steps:

the reference direction for determining the rotation direction of all the gears, the external splines, and the shafts to be clockwise or counterclockwise is the same, and as shown in fig. 1, the direction of the shaft center of the long output shaft 41 from the external spline E44 to the helical gear a43 is taken as a uniform reference direction, that is, from right to left in fig. 1 is taken as a uniform reference direction. In this reference direction, the rotation direction of the input shaft 21 and the helical gear H22 is clockwise, the rotation direction of the secondary rotating shaft 31, the helical gear K32 and the helical gear M33 is counterclockwise, the rotation direction of the long output shaft 41, the helical gear N42, the helical gear a43 and the external spline E44 is clockwise, the rotation direction of the idler shaft 51, the helical gear B52 and the helical gear C53 is counterclockwise, and the rotation direction of the short output shaft 61, the helical gear D62 and the external spline F63 is clockwise. In the method, the parameter related to the rotation direction is specified to be a positive value in a counterclockwise direction, and is specified to be a negative value in a clockwise direction. For example, if the angular error of helical gear a43 with respect to the external spline E44 is clockwise, the angular error is negative.

In step S1, the first output shaft system 4 is assembled, and the long output shaft 41 and the helical gear a43 of the present embodiment are positionally connected by a flat key. As shown in fig. 3, the design positions of the helical gear a43 and the male spline E44 are such that the symmetry line of the key slot, the symmetry line of one tooth profile of the helical gear a43 and the symmetry line of one tooth profile of the male spline E44 coincide. Because there is usually a certain machining error between the key slot on the long output shaft 41 and the tooth profile of the male spline E44, and between the key slot of the helical gear a43 and the tooth profile of the helical gear a43 during machining, and there is usually a certain assembly error during the assembly of the connection of the long output shaft 41 and the helical gear a43, these errors are accumulated together, and there is an angular error between the helical gear a43 and the male spline E44. The angular error value of the helical gear A43 and the external spline E44 measured by the coordinate measuring machine is 1 degree in the embodiment. As shown in FIG. 4, the angular error is recorded as φ from the external spline E44_AThat is, assuming the fixed external spline E44 (a series of oblique lines are drawn in the partial section of the external spline E44 in fig. 4 to indicate the assumed fixed external spline E44), the angular error of the helical gear a43 with respect to the external spline E44 is 1 degree clockwise, phi_A=1 degree.

When the middle shafting 5 is assembled, the bevel gear B52 and the bevel gear C53 of the embodiment are fixedly connected with the idler shaft 51 through flat keys. As shown in fig. 5, the design positions of the helical gear B52 and the helical gear C53 are the symmetry line of the key slot, the symmetry line of one tooth profile of the helical gear B52 and the symmetry line of one tooth profile of the helical gear C53 are coincident and in a vertical position, and the tooth profiles of the key slot, the helical gear B52 and the helical gear C53 are all located above the axial center of the idler shaft 51. Because certain errors exist in the machining and connecting assembly processes, the errors are accumulated together, and an angle exists between the bevel gear B52 and the bevel gear C53And (4) error. In the embodiment, the angular error values of the bevel gear B52 and the bevel gear C53 measured by the coordinate measuring machine are 0.9 degree. As shown in FIG. 6, the angular error is expressed as φ with respect to bevel gear B52_CThat is, if the helical gear B52 is assumed to be fixed (a part of the helical gear B52 in fig. 6 is partially drawn with a series of oblique lines to indicate that the helical gear B52 is assumed to be fixed), and the angular error of the helical gear C53 with respect to the helical gear B52 is 0.9 degrees counterclockwise, phi is_C=0.9 degree.

The second output shaft system 6 is assembled, and the short output shaft 61 and the bevel gear D62 of the present embodiment are positioned and connected by a flat key. As shown in fig. 7, the design positions of the helical gear D62 and the male spline F63 are such that the symmetry line of the key slot, the symmetry line of one tooth profile of the helical gear D62 and the symmetry line of one tooth profile of the male spline F63 coincide. There is an angular error between the helical gear D62 and the male spline F63 due to errors generated during machining and connection assembly. In the embodiment, the angular error value of the bevel gear D62 and the external spline F63 measured by the coordinate measuring machine is 1.5 degrees. As shown in FIG. 8, the angular error is expressed as φ with respect to the bevel gear D62_FThat is, if the helical gear D62 is assumed to be fixed (a part of the helical gear D62 in FIG. 8 is partially drawn with a series of oblique lines to indicate that the helical gear D62 is assumed to be fixed), and the error of the male spline F63 with respect to the helical gear D62 is 1.5 degrees clockwise, φ_F= 1.5 degrees.

And step S2, assembling the shafting, including the shafting with the measured angle error, on the box body 1. Wherein the male spline E44 and the male spline F63 are fitted in the same phase position as designed, and the end face of the male spline E44 of the long output shaft 41 and the end face of the male spline F63 of the short output shaft 61 are in the same plane.

Since the machining process generates angular errors, which usually cause phase deviation between the external spline E44 and the external spline F63, but the angular errors are relatively small as measured in the previous step, the same phase position can be assembled according to the design by using the key groove as a reference, as shown in fig. 9.

Step S3, calculate the angular error φ due to the external spline E44 and the helical gear A43_AThe angular deviation resulting in bevel gear B52 is noted as θ_BWhile the bevel gear C53 is alsoThe same amount of angular deviation occurs with the helical gear B52. The transmission ratio i = ω of the gear a and the gear b meshing with each other_a/ω_b=Z_b/Z_aAnd ω is_a=Δθ_a/Δt_a，ω_b=Δθ_b/Δt_bWherein ω is_aIs the angular velocity, ω, of gear a_bIs the angular velocity, Z, of gear b_aNumber of teeth of gear a, Z_bNumber of teeth of gear b, Δ θ_aFor gear a at Δ t_aAngle of rotation in time, Δ θ_bFor gear b at Δ t_bThe angle of rotation in time. The same time is used for the rotation of the gear a and the gear b which are in external engagement with each other, i.e. Δ t_a=Δt_bFrom which ω is derived_a/ω_b=（Δθ_a/Δt_a）/（Δθ_b/Δt_b）=Δθ_a/Δθ_b=Z_b/Z_a. For this embodiment, the angular error φ of helical gear A43 relative to the external spline E44_AIt can be seen that the external spline E44 is fixed and then the helical gear a43 is rotated around the axis by an angle phi_AAngle phi of rotation of bevel gear A43_ASimultaneously drives the bevel gear B52 to rotate by an angle theta_BSo that phi can be used_AInstead of Δ θ in the derived formula_aBy theta_BInstead of Δ θ in the derived formula_bIn addition to Z_AInstead of Z in the derived formula_a，Z_BInstead of Z in the derived formula_bIn addition, in the present embodiment, the parameters relating to the rotational direction are defined as positive and negative, and since the rotational directions of the helical gear A43 and the helical gear B52 are opposite, it is found that-phi_A/θ_B=Z_B/Z_AThat is to say-phi_AZ_A=θ_BZ_BFrom this, θ is derived_B=-φ_AZ_A/Z_B= - (-1) × 29/55=0.5273 degrees. For two gears meshing with each other, the number of teeth and the transmission ratio are constant, so the formula θ derived from the above is_B=-φ_AZ_A/Z_BAdapted for both standard gears and for gears with modified indexThe modified gear is suitable for both standard mounted gears and non-standard mounted gears.

The total angular deviation of bevel gear C53 is calculated and recorded as θ_C，θ_C=θ_B+φ_C=0.5273+0.9=1.4273 degrees. This formula can be understood as follows: assuming that the external spline E44 is held stationary, helical gear A43 has rotated an angle φ_AAngle phi of_ACausing bevel gear B52 and bevel gear C53 to rotate together at an angle θ_BThen holding bevel gear B52 stationary, as does external spline E44, and bevel gear C53 rotated an angle φ_CThen the total angular deviation θ of the helical gear C53_C=θ_B+φ_C. The outer spline E44 remains stationary at all times, the total angular deviation θ of the helical gear C53_CI.e., the angular offset of the helical gear C53 relative to the external spline E44.

Calculate the total angular deviation θ due to bevel gear C53_CThe angular deviation resulting in the helical gear D62 is noted as theta_DMeanwhile, the external spline F63 generates the same angular deviation with the helical gear D62, and the derivation process shows that theta is equal to theta_D=-θ_CZ_C/Z_D= -1.4273 × 55/29= -2.7069 degrees.

The total angular deviation of the male spline F63 is calculated and recorded as θ_F，θ_F=θ_D+φ_F= (-2.7069) + (-1.5) = -4.2069 degrees. As shown in FIG. 9, in accordance with the foregoing understanding process, the helical gear C53 is rotated an angle θ, assuming the external spline E44 remains stationary at all times_CAngle theta_CCausing helical gear D62 and male spline F63 to rotate together by an angle theta_DThen, keeping the helical gear D62 stationary, the external spline F63 rotates an angle phi_FThen the total angular deviation θ of the male spline F63_F=θ_D+φ_F. The outer spline E44 remains stationary at all times, the total angular deviation θ of the outer spline F63_FThat is, the angular deviation of the male spline F63 relative to the male spline E44, i.e., the total angular deviation θ of the male spline F63_FIs the actual phase deviation of the external spline E44 and the external spline F63, namely, the external spline F63 in the embodiment is relative to the external spline due to errors of machining assembly and the likeE44 was off-set 4.2069 degrees clockwise.

The direction of rotation required to adjust for the male spline F63 is opposite to the direction of the total angular misalignment of the male spline F63. The angle of the external spline F63 needing to be adjusted and rotated is recorded as gamma_{Regulating device}Then γ_{Regulating device}=-θ_F=4.2069 degrees.

The phase shift caused by the helical gear D62 for each tooth position of rotation resulting in the male spline F63 is calculated and recorded as Δ_DF，Δ_DF=360/Z_D-360/Z_F=360/29-360/28= -0.4433 degrees. Phase shift Δ in the present invention_DFWhether the calculated result is positive or negative is determined by the structures of the helical gear D and the external spline F on the short output shaft, the tooth numbers of the helical gear D and the external spline F are determined, and the phase shift delta is determined_DFWhether it is positive or negative is uniquely determined, and the phase shift Δ_DFWhether the number is positive or negative is not determined by the rotational direction of the helical gear D and the external spline F, and the phase shift Δ_DFWhether the number is positive or negative means that the direction of the phase shift by the external spline F is the same as or opposite to the direction of the rotational tooth position of the helical gear D. So despite the phase shift Δ_DFIs an angle value, but as an exception, the phase shift Δ_DFWhether it is positive or negative is determined by the structure. Phase shift Δ of the present embodiment_DFIs a negative number, which indicates that the phase of the external spline F63 is shifted by 0.4433 degrees clockwise every time the helical gear D62 is rotated counterclockwise by one tooth position; conversely, the phase of the male spline F63 is shifted counterclockwise by 0.4433 degrees every time the helical gear D62 is rotated one tooth position clockwise. Further, since the external spline F63 is shifted in phase from itself when the rotary helical gear D62 is adjusted, even if there is an angular error between the helical gear D62 and the external spline F63 due to machining or the like, the phase of the external spline F63 is still shifted clockwise by 0.4433 degrees every time the helical gear D62 is adjusted counterclockwise by one tooth position, and conversely, the phase of the external spline F63 is still shifted counterclockwise by 0.4433 degrees every time the helical gear D62 is adjusted clockwise by one tooth position. Fig. 10 is a front-rear comparison view showing that the helical gear D62 in this embodiment is rotated counterclockwise by one tooth position, and the helical gear D62 with the external spline F63 is rotated counterclockwise by one tooth position, and the phase of the external spline F63 is shifted clockwise by 0.4433 degrees.

Step S4, calculating the number of teeth of the helical gear D62 needing to be rotated by division, namely gamma_{Regulating device}Divided by Δ_DFThe obtained integer quotient is the tooth position number of the helical gear D62 needing to be adjusted and is recorded as n, and the obtained remainder is the residual adjustment rotation angle and is recorded as gamma_SurplusAnd hold γ_SurplusAnd gamma_{Regulating device}Positive and negative being equal, i.e. gamma_{Regulating device}/Δ_DF= 4.2069/(-0.4433) = -9 and 0.2172, i.e. n = -9, γ_Surplus=0.2172 degrees. The calculation result n is a negative number, and the calculation result n indicates the number of teeth of the helical gear D62 whose rotation needs to be adjusted, and is a parameter related to the rotation direction. That is, the rotating bevel gear D62 needs to be adjusted clockwise first by nine tooth positions and the remaining rotating angle γ needs to be adjusted_SurplusIt is adjusted by axially moving the short output shaft 61 and the helical gear D62. Calculating the phase offset Δ from the foregoing_DFCan also be concluded that_{Regulating device}Where the angle of =4.2069 degrees is a positive number, that is, the phase of the external spline F63 needs to be adjusted counterclockwise, the tooth position of the rotary helical gear D62 needs to be adjusted clockwise.

Calculating gamma_SurplusThe absolute value of (a) corresponds to the lead section length of the helical gear D62, which is the axial movement of the helical gear D62 and is marked as L_Surplus. The lead formula of the helical gear is L = pi × dp/tan beta, wherein L is the lead of the helical gear, dp is the pitch circle diameter of the helical gear, and beta is the helical angle of the helical gear. From this, the lead L of the helical gear D62 is shown_D=π*dp_D/tanβ_D= pi × 232/tan20=2002.4975 mm. Residual adjustment rotation angle gamma_SurplusThe absolute value of (D) corresponds to the axial movement amount L of the helical gear D62_Surplus=L_D*（∣γ_Surplus∣/360）=2002.4975*（∣0.2172∣/360）=1.2082mm。

The helical gear D62 will rotate inevitably when moving axially, and the rotation direction and the residual adjustment rotation angle gamma_SurplusThe corresponding rotation directions are the same. For the present embodiment, the remaining adjustment rotation angle γ_Surplus=0.2172 degrees, [ gamma ]_SurplusIs a positive number, corresponding to a rotation direction of the helical gear D6 which is moved in the counterclockwise direction, i.e. in the axial direction2, it is necessary to ensure that the bevel gear D62 rotates counterclockwise. Helical gear C53 is right-handed helical gear, helical gear D62 is left-handed helical gear, and helical gear D62 needs to be moved 1.2082mm axially to the left as shown in FIG. 1. That is, the axial moving direction of the helical gear D62 is determined by the helical direction and the residual adjusting rotation angle γ of the helical gear C53 and the helical gear D62_SurplusThe corresponding rotation direction is determined.

Step S5, keeping the phase position of the external spline E44 unchanged, adjusting and rotating the helical gear D62 clockwise by nine tooth positions, and then moving the short output shaft 61 with the helical gear D62 and the external spline F63 in the left axial direction by 1.2082 mm. After adjustment, the external spline F63 is retracted 1.2082mm leftwards relative to the external spline E44, namely the external spline F63 is axially dislocated 1.2082mm leftwards relative to the external spline E44, and when two screws of a double-screw extruder are connected, a gap sheet with the thickness of 1.2082mm can be added between the end face of the external spline F63 and the screws so as to offset the axial dislocated amount between the external spline E44 and the external spline F63.

If the number of teeth of the rotary helical gear D62 is not adjusted in the above method, but the short output shaft 61 and the helical gear D62 are directly axially moved to eliminate the actual phase deviation of the external spline E44 and the external spline F63, the external spline F63 needs to adjust the rotation angle γ_{Regulating device}The absolute value of (D) corresponds to the axial movement amount L of the helical gear D62_{Regulating device}=L_D*（∣γ_{Regulating device}| 360) =2002.4975 (| 4.2069 |/360) =23.4009 mm. That is, the short output shaft 61 and the helical gear D62 need to be moved by 23.4009mm in the axial direction, and obviously, the large axial movement amount causes the meshing contact surface between the helical gear C53 and the helical gear D62 to be greatly reduced, which affects the meshing effect between the helical gear C53 and the helical gear D62, shortens the service life of the helical gear C53 and the helical gear D62, reduces the torque transmission capability of the gear pair, and also causes the axial displacement amount between the end surface of the external spline E44 and the end surface of the external spline F63 to be large, which cannot be supplemented by the gap piece.

In the present embodiment, the external spline E44 and the external spline F63 are adjusted to the same phase position by adjusting the rotary helical gear D62 and axially moving the short output shaft 61, which inevitably results in one of the end surface of the external spline E44 of the long output shaft 41 and the end surface of the external spline F63 of the short output shaft 61The axial displacement is relatively small, and the amount of axial displacement L between the end face of the male spline F63 and the end face of the screw increases when the screw is connected_SurplusThe same thickness of the gap piece.

The design positions of the end face of the external spline E44 and the end face of the external spline F63 in this embodiment are in the same plane, and the design positions of the external spline E44 and the external spline F63 are in the same phase, but a certain phase deviation occurs between the external spline E44 and the external spline F63 due to a certain error in the machining and assembling process. Adjusting the same phase according to the method of the present embodiment can make the amount of axial misalignment between the end face of the male spline E44 and the end face of the male spline F63 small. More importantly, the method according to the embodiment adjusts the same phase without modifying the internal structure of the existing gear box, does not need to increase more connections or matching relations, does not improve the material and process cost, ensures the torque transmission capacity of the gear pair, and is applicable to low-speed and high-speed extruders.

Example two:

the present embodiment is still illustrated by taking the gear box of the twin-screw extruder as an example in the first embodiment, and the related angle error in the first embodiment is used, and the related parameter of the bevel gear B52, namely the pitch diameter dp of the bevel gear B52 when the bevel gear A43 and the bevel gear B52 are meshed, is supplemented_B=770mm。

In the method for assembling and phase adjusting the equidirectional output structure according to the present embodiment, on the basis of the first embodiment, it is considered that the gear pair normally has a backlash in the operating state, and the backlash can be regarded as an assembly error, so the method includes, after step S2 in the first embodiment, step S21: the circumferential backlash between bevel gear A43 and bevel gear B52 was measured and is denoted j_ABThe circumferential backlash of the gear pair is an arc length, so j_ABAlways positive, and the circumferential backlash j is measured by a dial indicator_AB=0.55 mm. Side of circumferenceThe backlash is the maximum of the pitch arc length that one gear can rotate through while the other gear is fixed in a pair of gears meshed with each other. As shown in fig. 11 and 12, the present invention is based on operating conditions and only needs to calculate the circumferential backlash by half, or only the profile one-sided circumferential backlash. The backlash angle at which the helical gear B needs to rotate when the helical gear A is used as a reference to cancel out the tooth profile single-sided circumferential backlash of the helical gear B based on the operating state is recorded as mu_BAnd simultaneously, the bevel gear C also rotates along with the bevel gear B by the same angle. The arc length formula is L = n pi r/180, which corresponds to the invention as (j)_AB/2）=μ_B*π*（dp_B/2)/180, since the parameters relating to the direction of rotation in the present invention define positive and negative values, but the backlash angle μ_BIs determined according to the relative rotation direction, so the side clearance angle mu is temporarily determined_B=+/-（j_AB/dp_B) (180/π). According to the method for determining the positive and negative values in the first embodiment, as shown in FIG. 11, based on the operation status and with the bevel gear A43 as the reference, that is, the bevel gear A43 is the drive wheel rotating clockwise, if the bevel gear A43 is assumed to be fixed, the circumferential backlash j is cancelled_ABThen helical gear B52 needs to rotate clockwise, i.e. helical gear B52 needs to rotate the backlash angle mu_BIs negative, the backlash angle μ of the present embodiment_B=-（j_AB/dp_B) (180/pi) = - (0.55/770) × (180/pi) = -0.0409 degrees.

Circumferential backlash between bevel gear C53 and bevel gear D62 is measured and is denoted j_CDMeasuring the circumferential backlash j by using a dial indicator_CD=0.32 mm. The backlash angle at which the helical gear D needs to rotate when the helical gear C is used as a reference to cancel out the tooth profile single-sided circumferential backlash of the helical gear D based on the operating state is expressed as mu_DThen temporarily determine the side clearance angle mu_D=+/-（j_CD/dp_D) (180/pi) and the external splines F also rotate by the same amount of angle with the helical gear D. For this embodiment, according to the method for determining the positive and negative values in the first embodiment, as shown in fig. 12, based on the operation status and using the bevel gear C53 as the reference, that is, the bevel gear C53 is the counterclockwise driving wheel, if the bevel gear C53 is assumed to be fixed, the circle is offsetPeripheral side gap j_CDThe helical gear D62 needs to rotate counterclockwise, i.e. the backlash angle μ by which helical gear D62 needs to rotate_DA positive value, then μ_D=（j_CD/dp_D) (180/pi) = (0.32/232) × (180/pi) =0.079 degrees.

Step S3 of the present embodiment is: calculate the angular error φ due to the external spline E44 and the helical gear A43_AThe angular deviation resulting in bevel gear B52 is noted as θ_B，θ_B=-φ_AZ_A/Z_B= - (-1) × 29/55=0.5273 degrees, while the helical gear C53 also produces an angular deviation of the same magnitude as the helical gear B52.

The total angular deviation of bevel gear C53 is calculated and recorded as θ_C，θ_C=θ_B+μ_B+φ_C=0.5273+ (-0.0409) +0.9= 1.3864. This formula can be understood as follows: assuming that the external spline E44 is held stationary, helical gear A43 has rotated an angle φ_AAngle phi of_ACausing bevel gear B52 and bevel gear C53 to rotate together at an angle θ_BThen keeping bevel gear A43 still, bevel gear B52 and bevel gear C53 rotate together by an angle mu_BThen holding bevel gear B52 stationary, as does external spline E44, and bevel gear C53 rotated an angle φ_CThen the total angular deviation θ of the helical gear C53_C=θ_B+μ_B+φ_C。

Calculate the total angular deviation θ due to bevel gear C53_CThe angular deviation resulting in the helical gear D62 is noted as theta_DMeanwhile, the external spline F63 generates the same angular deviation with the helical gear D62, and the derivation process shows that theta is equal to theta_D=-θ_CZ_C/Z_D= -1.3864 × 55/29= -2.6294 degrees.

The total angular deviation of the male spline F63 is calculated and recorded as θ_F，θ_F=θ_D+μ_D+φ_F= (-2.6294) +0.079+ (-1.5) = -4.0504 degrees. Following the foregoing understanding process, the helical gear C53 is rotated an angle θ, assuming the external spline E44 remains stationary at all times_CAngle theta_CCauses the helical gear D62 and the external spline F63 to rotate togetherAn angle theta_DThen keeping the helical gear C53 still, the helical gear D62 and the external spline F63 rotate together by an angle mu_DThen keeping the helical gear D62 still and the external spline F63 rotates by an angle phi_FThen the total angular deviation θ of the male spline F63_F=θ_D+μ_D+φ_FTotal angular deviation θ of the male spline F63_FNamely, the actual phase deviation of the external spline E44 and the external spline F63, namely, the deviation of the external spline F63 in the present embodiment from the external spline E44 clockwise by 4.0504 degrees during actual operation due to errors such as machining and assembling.

The direction of rotation required to adjust for the male spline F63 is opposite to the direction of the total angular misalignment of the male spline F63. The angle of the external spline F63 needing to be adjusted and rotated is recorded as gamma_{Regulating device}Then γ_{Regulating device}=-θ_F=4.0504 degrees.

The phase shift caused by the helical gear D62 for each tooth position of rotation resulting in the male spline F63 is calculated and recorded as Δ_DF，Δ_DF=360/Z_D-360/Z_F=360/29-360/28= -0.4433 degrees.

Step S4, calculating the number of teeth of the helical gear D62 needing to be rotated by division, namely gamma_{Regulating device}Divided by Δ_DFThe obtained integer quotient is the tooth position number of the helical gear D62 needing to be adjusted and is recorded as n, and the obtained remainder is the residual adjustment rotation angle and is recorded as gamma_SurplusAnd hold γ_SurplusAnd gamma_{Regulating device}Positive and negative being equal, i.e. gamma_{Regulating device}/Δ_DF= 4.0504/(-0.4433) = -9 and 0.0607, i.e. n = -9, γ_Surplus=0.0607 degrees, the calculation result n is negative number, that is, nine tooth positions of the rotating bevel gear D62 need to be adjusted clockwise first, and the remaining adjustment rotation angle γ_SurplusIt is adjusted by axially moving the short output shaft 61 and the helical gear D62.

Calculating gamma_SurplusThe absolute value of (a) corresponds to the lead section length of the helical gear D62, which is the axial movement of the helical gear D62 and is marked as L_Surplus. As can be seen from the calculation of the first embodiment, the lead L of the helical gear D62_D=2002.4975 mm. Residual adjustment rotation angle gamma_SurplusThe absolute value of (D) corresponds to the axial direction of the helical gear D62Amount of movement L_Surplus=L_D*（∣γ_Surplus∣/360）=2002.4975*（∣0.0607∣/360）=0.3376mm。

In the embodiment, the number of teeth n = -9 for the helical gear D62 to adjust, nine teeth positions of the rotating helical gear D62 need to be adjusted clockwise, and the remaining adjustment rotation angle γ after the external spline F63 needs to adjust the angle 4.0504 degrees and passes through nine teeth positions of the rotating helical gear D62 clockwise_Surplus0.0607 degrees, the residual adjustment rotation angle gamma_SurplusThe corresponding rotational direction is counterclockwise for positive numbers, i.e. it is necessary to ensure that the helical gear D62 rotates counterclockwise when the helical gear D62 is moved axially. Helical gear C53 is right-handed helical gear, helical gear D62 is left-handed helical gear, and helical gear D62 needs to be moved 0.3376mm axially to the left as shown in FIG. 1.

Step S5, keeping the phase position of the external spline E44 unchanged, adjusting and rotating the helical gear D62 clockwise by nine tooth positions, and then axially moving the short output shaft 61 with the helical gear D62 and the external spline F63 leftward by 0.3376mm as shown in fig. 1. After adjustment, the external spline F63 is retracted 0.3376mm leftwards relative to the external spline E44, namely the external spline F63 is axially dislocated 0.3376mm leftwards relative to the external spline E44, and when two screws of a double-screw extruder are connected, a gap sheet with the thickness of 0.3376mm can be added between the end face of the external spline F63 and the screws so as to offset the axial dislocated amount between the external spline E44 and the external spline F63.

The method for assembling and adjusting the phase of the unidirectional output structure of the present embodiment, in addition to the advantages of the first embodiment, also takes into account the backlash, i.e., the adjustment is performed based on the operating condition, so that it is ensured that the same phase output by the male spline E44 and the male spline F63 in the operating condition is more accurate.

If there is a small phase deviation of the angle due to other reasons after the adjustment method according to the invention, it can also be eliminated by trying to move the short output shaft and the helical gear D and the external spline F thereon axially, which is much simpler than the prior art method of directly trying to adjust the rotational tooth position and move it axially, i.e. the adjustment method according to the invention provides at least a basis for readjustment.

Example three:

fig. 13 is a schematic diagram of a partial internal structure of a gear box of a twin-screw extrusion granulator in the prior art, which is also a twin-screw extruder, and the gear box of the twin-screw extrusion granulator includes a box body (not shown), an input shaft system 7, a first output shaft system 8, an intermediate shaft system 9, and a second output shaft system 10.

The input shaft system 7 includes an input shaft 71 rotatably connected to the housing and a helical gear S72 fixed to the input shaft 71. The left end of the input shaft 71 in fig. 13 is exposed to the left side of the case for connection to an external motor. The first output shafting 8 includes a long output shaft 81 rotatably connected to the case and a bevel gear T82 and a bevel gear a83 fixed to the long output shaft 81. The middle shafting 9 comprises an idler shaft 91 rotationally connected to the box body, and a bevel gear B92 and a left-handed bevel gear C93 which are fixed on the idler shaft 91. The second output shaft system 10 includes a short output shaft 101 rotatably coupled to the case and a right-hand helical gear D102 fixed to the short output shaft 101. The axes of the input shaft 71, the long output shaft 81, the idler shaft 91 and the short output shaft 101 are parallel to each other, the helical gear S72 is externally meshed with the helical gear T82, the helical gear A83 is externally meshed with the helical gear B92, and the helical gear C93 is externally meshed with the helical gear D102. The long output shaft 81 and the short output shaft 101 have the same output direction and the same output rotation speed. The output end of the long output shaft 81 is provided with an integrally formed external spline E84, and the output end of the short output shaft 101 is provided with an integrally formed external spline F103. The external spline E84 and the external spline F103 are the same in shape, and as shown in FIG. 13, the external spline E84 and the external spline F103 are exposed on the right side of the box body and are used for being in splined connection with two screws of the twin-screw extrusion granulator.

The torque transfer direction in this gearbox is input shaft 71 to long output shaft 81, long output shaft 81 to idler shaft 91, idler shaft 91 to short output shaft 101. As shown in fig. 13, the design positions of the end surface of the external spline E84 and the end surface of the external spline F103 are on the same plane. As shown in fig. 14, the phase design positions of the external spline E84 and the external spline F103 are in phase. For the convenience of understanding, the short output shaft 101 and the bevel gear D102 and the external spline F103 thereon are shown in fig. 14 rotated at an angle relative to the bevel gear B92, but the actual structure is not changed, and the method of the present invention is not affected at all. The same phase design positions of the external spline E84 and the external spline F103 shown in fig. 14 are: the line of symmetry of the keyway of helical gear a83, the line of symmetry of a tooth profile of helical gear a83 and the line of symmetry of a tooth profile of the male spline E84 are coincident and in a vertical position, and the keyway of helical gear a83, the tooth profile of helical gear a83 and the tooth profile of the male spline E84 are all above the axial center of the male spline E84; the symmetry line between the two tooth profiles of the helical gear D102 and the symmetry line of one tooth profile of the external spline F103 are coincident and in a vertical position, and the two tooth profiles of the helical gear D102 and the tooth profile of the external spline F103 are both located above the axial center of the external spline F103. The center-to-center distance between the long output shaft 81 and the idler shaft 91 is equal to the sum of the pitch circle radius of bevel gear a83 and the pitch circle radius of bevel gear B92, i.e., the center-to-center distance between bevel gear a83 and bevel gear B92 is the standard center-to-center distance. The center distance between the idler shaft 91 and the short output shaft 101 is equal to the sum of the pitch circle radius of the bevel gear C93 and the pitch circle radius of the bevel gear D102, that is, the center distance between the bevel gear C93 and the bevel gear D102 is the standard center distance.

In the embodiment, relevant parameters such as gears, external splines, gear engagement and the like in the gearbox are listed one by one for subsequent calculation. Helical gear A83 has Z teeth_AAnd the number of teeth of helical gear D102 is denoted as Z_D，Z_A=Z_D= 24. The number of teeth of helical gear B92 is denoted as Z_BAnd the number of teeth of the helical gear C93 is represented as Z_C，Z_B=Z_C= 52. The number of teeth of the external spline E84 is Z_EThe number of teeth of the male spline F103 is denoted as Z_F，Z_E=Z_FAnd = 25. The pitch circle diameter of helical gear B92 when helical gear A83 and helical gear B92 are engaged is designated dp_B，dp_B=416 mm. The pitch circle diameter of the helical gear D102 when the helical gear C93 meshes with the helical gear D102 is denoted as dp_D，dp_D=120 mm. The helix angle of helical gear D102 is noted as β_D，β_D=9 degrees.

the reference direction for determining the rotation direction of all the gears, the external splines, and the shafts to be clockwise or counterclockwise is the same, and as shown in fig. 13, the direction of the shaft center of the long output shaft 81 from the external spline E84 to the helical gear a83 is taken as a uniform reference direction, that is, the direction from right to left in fig. 13 is taken as a uniform reference direction. In this reference direction, the rotation direction of the input shaft 71 and the helical gear S72 is clockwise, the rotation direction of the long output shaft 81, the helical gear T82, the helical gear a83 and the external spline E84 is counterclockwise, the rotation direction of the idler shaft 91, the helical gear B92 and the helical gear C93 is clockwise, and the rotation direction of the short output shaft 101, the helical gear D102 and the external spline F103 is counterclockwise. In the method, the parameter related to the rotation direction is specified to be a positive value in a counterclockwise direction, and is specified to be a negative value in a clockwise direction. For example, if the angular error of helical gear a83 with respect to the external spline E84 is clockwise, the angular error is negative.

In step S1, the first output shaft system 8 is assembled, and the long output shaft 81 and the helical gear a83 of the present embodiment are positionally connected by a flat key. As shown in fig. 15, the design positions of the helical gear a83 and the male spline E84 are such that the symmetry line of the key slot, the symmetry line of one tooth profile of the helical gear a83 and the symmetry line of one tooth profile of the male spline E84 coincide. Because there is usually a certain machining error between the key slot on the long output shaft 81 and the tooth profile of the male spline E84, and also between the key slot of the helical gear a83 and the tooth profile of the helical gear a83 during machining, and also there is usually a certain assembly error during the assembly of the connection of the long output shaft 81 and the helical gear a83, these errors are accumulated together, and an angular error exists between the helical gear a83 and the male spline E84. The angular error value of the helical gear A83 and the external spline E84 measured by the coordinate measuring machine in the embodiment is 0.48 degrees. As shown in FIG. 16, the angular error is recorded as φ from the external spline E84_AThat is, assuming that the external spline E84 is fixed (a series of oblique lines are drawn in the part of the external spline E84 in fig. 16 to indicate that the external spline E84 is fixed), the angular error of the helical gear a83 with respect to the external spline E84 is 0.48 degrees counterclockwise, phi is_A=0.48 degrees.

The middle shafting 9 is assembled, and the bevel gear B92 and the bevel gear C93 of the embodiment are connected with the idler shaft 91 in a positioning way through flat keys. As shown in FIG. 17, the design positions of bevel gear B92 and bevel gear C93 are keysThe symmetry line of the groove, the symmetry line between the two tooth profiles of the bevel gear B92 and the symmetry line of one tooth profile of the bevel gear C93 coincide and are in a vertical position, and the two tooth profiles of the keyway, the bevel gear B92 and the tooth profile of the bevel gear C93 are all located above the axial center of the idler shaft 91. Due to certain errors in the machining and connection assembly processes, these errors are accumulated together, and an angular error exists between the bevel gear B92 and the bevel gear C93. In the embodiment, the angular error values of the bevel gear B92 and the bevel gear C93 measured by the coordinate measuring machine are 0.1 degree. As shown in FIG. 18, the angular error is expressed as φ with respect to the bevel gear B92_CThat is, if the helical gear B92 is assumed to be fixed (a part of the helical gear B92 in fig. 18 is partially drawn with a series of oblique lines to indicate that the helical gear B92 is assumed to be fixed), the angular error of the helical gear C93 with respect to the helical gear B92 is 0.1 degrees clockwise, and then Φ is set to be equal to_C=0.1 degree.

The second output shaft system 10 is assembled, and the short output shaft 101 and the helical gear D102 of the present embodiment are integrally formed. As shown in fig. 19, the helical gear D102 and the male spline F103 are designed in such a position that the line of symmetry between the two tooth profiles of the helical gear D102 and the line of symmetry of one tooth profile of the male spline F103 coincide. There is an angular error between the helical gear D102 and the external spline F103 due to an error generated during the machining process. In the embodiment, the angular error value of the helical gear D102 and the external spline F103 measured by the coordinate measuring machine is 0.31 degree. As shown in FIG. 20, the angle error is expressed as φ with respect to the bevel gear D102_FThat is, if the helical gear D102 is assumed to be fixed (a part of the helical gear D102 in FIG. 20 is shown by a series of oblique lines, and if the helical gear D102 is assumed to be fixed), the error of the external spline F103 with respect to the helical gear D102 is 0.31 degrees counterclockwise, φ_F=0.31 degrees.

In the embodiment, the axial machining and assembling errors of the shafts and the gears are easy to control relative to the angle errors, and the axial machining and assembling errors are small. Axial machining errors of the shafts, the gears, steps, spigots and the like on the shafts and the gears are ensured to be within a tolerance range, and phase deviation caused by the machining errors can be ignored. For the axial assembly error, the assembly and measurement can be carried out during the assembly of each independent shafting, so that the assembly error is reduced to be within an allowable range, even eliminated, and the phase deviation caused by the axial assembly error can be ignored.

And step S2, assembling the shafting, including the shafting with the measured angle error, on the box body. Wherein the external spline E84 and the external spline F103 are fitted in the same phase position as designed, and the end face of the external spline E84 and the end face of the external spline F103 are in the same plane.

As described above, the angular errors generated during the machining assembly usually cause the phase deviation between the external spline E84 and the external spline F103, but these angular errors are relatively small as measured in the previous step, so as shown in fig. 21, the external spline E84 can be assembled according to the designed position by using the key groove as a reference, that is, the aforementioned symmetry line of the tooth profile of the external spline E84 is in the vertical position, while the external spline F103 is not provided on the short output shaft 101, and a reference line can be made on the end surface of the external spline F103, for example, the symmetry line of the tooth profile of the external spline F103 is drawn on the end surface of the external spline F103, and when the external spline E84 and the external spline F103 are assembled according to the designed in-phase position, the symmetry line should be close to the vertical position. In other embodiments, the alignment assembly can be performed by taking reference lines on the end faces of the external spline E84 and the external spline F103.

Step S21: the circumferential backlash between bevel gear A83 and bevel gear B92 was measured and is denoted j_ABMeasuring the circumferential backlash j by using a dial indicator_AB=0.35 mm. As shown in fig. 22 and 23, the present invention is based on the consideration of the operating condition, and only the tooth profile single-side circumferential backlash is considered. The backlash angle at which the helical gear B needs to rotate when the helical gear A is used as a reference to cancel out the tooth profile single-sided circumferential backlash of the helical gear B based on the operating state is recorded as mu_BThen temporarily determine the side clearance angle mu_B=+/-（j_AB/dp_B) (180/pi) and the helical gear C rotates with the helical gear B by the same angle. In the present embodiment, according to the method for determining the positive and negative values, as shown in fig. 22, based on the operation status and using the bevel gear a83 as the reference, that is, the bevel gear a83 is the drive wheel rotating counterclockwise, if the bevel gear a83 is assumed to be fixed, the circumferential backlash j is cancelled_ABIt is required that the helical gear B92 rotate counterclockwise,i.e. the backlash angle mu at which the bevel gear B92 needs to rotate_BA positive value, the backlash angle μ of the present embodiment_B=（j_AB/dp_B) (180/pi) = (0.35/416) × (180/pi) =0.0482 degrees.

The circumferential backlash between bevel gear C93 and bevel gear D102 is measured and is denoted j_CDMeasuring the circumferential backlash j by using a dial indicator_CD=0.25 mm. The backlash angle at which the helical gear D needs to rotate when the helical gear C is used as a reference to cancel out the tooth profile single-sided circumferential backlash of the helical gear D based on the operating state is expressed as mu_DThen temporarily determine the side clearance angle mu_D=+/-（j_CD/dp_D) (180/pi) and the external splines F also rotate by the same amount of angle with the helical gear D. In the present embodiment, according to the method for determining the positive and negative values, as shown in FIG. 23, based on the operation status and using the bevel gear C93 as the reference, that is, the bevel gear C93 is the driving wheel rotating clockwise, if the bevel gear C93 is assumed to be fixed, the circumferential backlash j is cancelled_CDThe helical gear D102 needs to rotate clockwise, i.e. the backlash angle μ by which the helical gear D102 needs to rotate_DA negative value, then μ_D=-（j_CD/dp_D) (180/pi) = - (0.25/120) × (180/pi) = -0.1194 degrees.

Step S3, calculate the angular error φ due to the external spline E84 and the helical gear A83_AThe angular deviation resulting in bevel gear B92 is noted as θ_B，θ_B=-φ_AZ_A/Z_BAnd the angular deviation of the helical gear C93 is the same as that of the helical gear B92 while the angular deviation of the helical gear C is-0.48 × 24/52= -0.2215 degrees.

The total angular deviation of bevel gear C93 is calculated and recorded as θ_C，θ_C=θ_B+μ_B+φ_C= -0.2215+0.0482+ (-0.1) = -0.2733. This formula can be understood as follows: assuming that the external spline E84 is held stationary, helical gear A83 has rotated an angle φ_AAngle phi of_ACausing bevel gear B92 and bevel gear C93 to rotate together at an angle θ_BThen keeping bevel gear A83 still, bevel gear B92 and bevel gear C93 rotate together by an angle mu_BThen keeping the helical gear B92 and the external spline E84 in placeThe bevel gear C93 rotates by an angle phi_CThen the total angular deviation θ of the helical gear C93_C=θ_B+μ_B+φ_C。

Calculate the total angular deviation θ due to bevel gear C93_CThe angular deviation caused by the helical gear D102 is noted as theta_D，θ_D=-θ_CZ_C/Z_D= 0.2733 × 52/24=0.5922 degrees, and the external spline F103 also produces an angular deviation of the same magnitude as the helical gear D102.

The total angular deviation of the male spline F103 is calculated and recorded as θ_F，θ_F=θ_D+μ_D+φ_F=0.5922+ (-0.1194) +0.31=0.7828 degrees. Following the foregoing understanding process, the helical gear C93 is rotated an angle θ, assuming the external spline E84 remains stationary at all times_CAngle theta_CCausing helical gear D102 and external spline F103 to rotate together by an angle theta_DThen keeping the bevel gear C93 still, the bevel gear D102 and the external spline F103 rotate together by an angle mu_DThen the helical gear D102 is kept still and the external spline F103 is rotated by an angle phi_FThen the total angular deviation θ of the male spline F103_F=θ_D+μ_D+φ_FTotal angular deviation θ of the male spline F103_FNamely, the actual phase deviation of the external spline E84 and the external spline F103, namely, the counterclockwise deviation 0.7828 degrees of the external spline F103 relative to the external spline E84 in the embodiment is caused during actual operation due to errors of machining, assembling and the like.

The direction in which the external spline F103 needs to be rotated is opposite to the direction of the total angular deviation of the external spline F103. The angle of the external spline F103 needing to be adjusted and rotated is recorded as gamma_{Regulating device}Then γ_{Regulating device}=-θ_F= -0.7828 degrees.

The phase shift caused by the external spline F103 per one tooth position of the helical gear D102 is calculated and recorded as delta_DF，Δ_DF=360/Z_D-360/Z_F=360/24-360/25=15-14.4=0.6 degrees. The phase shift Δ_DFIs a positive number, which indicates that the phase of the external spline F103 is counterclockwise when the helical gear D102 is rotated by one tooth position every counterclockwise adjustmentOffset by 0.6 degrees; conversely, the phase of the external spline F103 is shifted clockwise by 0.6 degrees every time the helical gear D102 is rotated by one tooth position by clockwise adjustment. Fig. 24 is a front-rear comparison view showing that the helical gear D102 of the present embodiment is rotated counterclockwise by one tooth position, and the helical gear D102 and the external spline F103 are rotated counterclockwise by one tooth position, and then the phase of the external spline F103 is shifted counterclockwise by 0.6 degrees.

Step S4, calculating the number of teeth of the helical gear D102 needing to be rotated by division, i.e. γ_{Regulating device}Divided by Δ_DFThe obtained integer quotient is the number of teeth positions of the helical gear D102 needing to be adjusted and is recorded as n, and the obtained remainder is the residual adjustment rotation angle and is recorded as gamma_SurplusAnd hold γ_SurplusAnd gamma_{Regulating device}Positive and negative being equal, i.e. gamma_{Regulating device}/Δ_DF= 0.7828/0.6= -1 or more-0.1828, i.e. n = -1, γ_Surplus= -0.1828 degrees, the calculation result n is negative number, that is, it is necessary to adjust one tooth position of the rotating bevel gear D102 clockwise first, and the remaining adjustment rotation angle γ_SurplusIt is adjusted by axially moving the short output shaft 101 and the helical gear D102.

Calculating gamma_SurplusThe absolute value of (a) corresponds to the lead section length of the helical gear D102, which is the axial movement amount of the helical gear D102 and is marked as L_Surplus. Lead L of helical gear D102_D=π*dp_D/tanβ_D= pi 120/tan9= 2380.2282. Residual adjustment rotation angle gamma_SurplusThe axial movement amount L of the helical gear D102 corresponding to the absolute value of (A)_Surplus=L_D*（∣γ_Surplus∣/360）=2380.2282*（∣0.1828∣/360）=1.2086mm。

In the embodiment, the number n = -1 of the tooth positions of the helical gear D102 needing to be adjusted, one tooth position of the helical gear D102 needing to be adjusted clockwise, and the angle-0.7828 degrees of the external spline F103 needing to be adjusted pass through the remaining adjustment rotation angle γ after one tooth position of the helical gear D102 needing to be adjusted clockwise_SurplusAt-0.1828 degrees, the remaining adjustment rotation angle gamma_SurplusThe negative number corresponds to a clockwise rotation direction, i.e. when the helical gear D102 is moved axially, it is necessary to ensure that the helical gear D102 rotates clockwise. Bevel gear C93 is a left-handed bevel gear, and bevel gear D102 is a right-handed bevel gearThe helical gear D102 is moved 1.2086mm axially to the left as shown in fig. 13.

Step S5, keeping the phase position of the external spline E84 unchanged, rotating the helical gear D102 clockwise by one tooth position, and then moving the short output shaft 101 with the helical gear D102 and the external spline F103 to the left axial direction by 1.2086 mm. After adjustment, the outer spline F103 retracts 1.2086mm leftwards relative to the outer spline E84, namely the outer spline F103 is axially displaced 1.2086mm leftwards relative to the outer spline E84, and when two screws of a twin-screw extrusion granulator are connected, a gap piece with the thickness of 1.2086mm can be added between the end face of the outer spline F103 and the screws so as to offset the axial displacement between the outer spline E84 and the outer spline F103.

If the number of teeth of the rotary helical gear D102 is not adjusted in the above method, but the short output shaft 101 and the helical gear D102 are directly axially moved to eliminate the actual phase deviation between the external spline E84 and the external spline F103, the external spline F103 needs to be adjusted by the rotation angle γ_{Regulating device}The axial movement amount L of the helical gear D102 corresponding to the absolute value of (A)_{Regulating device}=L_D*（∣γ_{Regulating device}| 360) =2380.2282 (| 0.7828 |/360) =5.1757 mm. That is, the short output shaft 101 and the helical gear D102 need to be axially moved by 5.1757mm, and obviously, the large axial movement amount greatly reduces the meshing contact surface between the helical gear C93 and the helical gear D102, affects the meshing effect between the helical gear C93 and the helical gear D102, shortens the service life of the helical gear C93 and the helical gear D102, reduces the torque transmission capability of the gear pair, and makes the axial displacement amount between the end surface of the external spline E84 and the end surface of the external spline F103 large, so that the gap piece cannot be used for repairing.

In the embodiment, the external spline E84 and the external spline F103 are adjusted to be in the same phase position by adjusting the rotating bevel gear D102 and axially moving the short output shaft 101, and after the short output shaft 101 is axially moved, an axial misalignment is inevitably generated between the end surface of the external spline E84 and the end surface of the external spline F103, but the axial misalignment is relatively small, and the axial movement amount L and the increase between the end surface of the external spline F103 and the end surface of the screw when the screw is connected are small_SurplusThe same thickness of the gap piece.

The design positions of the end surface of the external spline E84 and the end surface of the external spline F103 in this embodiment are in the same plane, and the design positions of the external spline E84 and the external spline F103 are in the same phase, but a certain phase deviation occurs between the external spline E84 and the external spline F103 due to a certain error in the process of machining and assembling. Adjusting the same phase according to the method of the present embodiment makes it possible to make the amount of axial misalignment between the end face of the external spline E84 and the end face of the external spline F103 small. More importantly, adjust the same phase according to the method of this embodiment and need not reform transform current gear box inner structure, need not increase more connections or cooperation relation, can not improve material and processing cost, and ensured the moment of torsion transmissibility of gear pair, low-speed and high-speed twin-screw extrusion granulator can both be suitable for, in addition because be the result that obtains through precision measurement and calculation, adjust according to the result that draws, so need not dismantle the reassembling repeatedly to each shafting or gear etc. greatly reduced adjusts the degree of difficulty, shorten assembly adjustment time, manpower and materials are saved greatly. In addition, the present embodiment also takes into account backlash, i.e., adjustment based on the operating state, which ensures that the same phase output by the male spline E84 and the male spline F103 in the operating state is more accurate.

The above are only three specific embodiments of the present invention, but the design concept of the present invention is not limited thereto, and any insubstantial modifications made by the design concept of the present invention fall within the protection scope of the present invention.

Claims

1. The assembly and phase adjustment method of the same-direction output structure comprises a box body, a first output shaft system, an intermediate shaft system and a second output shaft system, wherein the first output shaft system comprises a first output shaft rotationally connected to the box body and a gear A fixed on the first output shaft, the intermediate shaft system comprises an idler shaft rotationally connected to the box body, a gear B and a gear C fixed on the idler shaft, the second output shaft system comprises a second output shaft rotationally connected to the box body and a gear D fixed on the second output shaft, the gear A and the gear B are externally meshed, the gear C and the gear D are helical gears which are externally meshed with each other, the torque transmission direction is that the first output shaft system transmits the torque to the intermediate shaft system, and the intermediate shaft system transmits the torque to the intermediate shaft systemThe output shaft system comprises a second output shaft system, the axes of a first output shaft and a second output shaft are parallel, the output direction and the output speed are the same, the output end of the first output shaft is provided with an external spline E, the output end of the second output shaft is provided with an external spline F, the external spline E and the external spline F are the same in shape, the design positions of the end face of the external spline E of the first output shaft and the end face of the external spline F of the second output shaft are on the same plane, the design positions of the external spline E and the external spline F are in the same phase, the number of teeth of a gear A is recorded as Z_AThe number of teeth of gear B is denoted as Z_BNumber of teeth of gear C is denoted as Z_CThe number of teeth of gear D is noted as Z_DAnd the number of teeth of the external spline F is represented as Z_FCharacterised by the fact that Z_DAnd Z_FNot equal, the method comprises:

step S3, calculating the angle error phi of the external spline E and the gear A_AThe angular deviation resulting from gear B is noted as θ_B，θ_B=-φ_A*（Z_A/Z_B) (ii) a The total angular deviation of gear C is calculated and recorded as θ_C，θ_C=θ_B+φ_C(ii) a Calculating the total angular deviation theta due to the gear C_CThe angular deviation caused by the gear D is notedθ_D，θ_D=-θ_C*（Z_C/Z_D) (ii) a The total angular deviation of the male spline F is calculated and recorded as θ_F，θ_F=θ_D+φ_F(ii) a The direction of the external spline F needing to be adjusted and rotated is opposite to the direction of the total angular deviation of the external spline F, and the angle of the external spline F needing to be adjusted and rotated is recorded as gamma_{Regulating device}Then γ_{Regulating device}=-θ_FCalculating the phase shift of the external spline F caused by each tooth position of the gear D and recording the phase shift as delta_DF，Δ_DF=360/Z_D-360/Z_F；

2. The method for assembling and phasing a co-rotating output structure of claim 1, wherein step S2 is followed by step S21 of measuring the circumferential backlash between gear a and gear B and recording as j_ABThe backlash angle at which the gear B needs to rotate when the gear A cancels the tooth profile single-sided circumferential backlash based on the operating state is represented as μ_BThen μ_B=+/-（j_AB/dp_B) (180/pi); measuring the circumferential backlash between gear C and gear D and recording j_CDOffset based on operating conditions and with reference to gear CThe backlash angle at which the gear D needs to rotate when the gear C has a single-sided circumferential backlash of the tooth profile is recorded as mu_DThen μ_D=+/-（j_CD/dp_D) (180/pi); wherein dp_BIs the pitch diameter, dp, of gear B_DIs the pitch diameter of the gear D, the backlash angle mu_BAnd the backlash angle mu_DIs determined according to the method of claim 1;