CN112128350B

CN112128350B - Same-phase assembly adjustment method for parallel and same-direction output structure

Info

Publication number: CN112128350B
Application number: CN202010856713.3A
Authority: CN
Inventors: 张坤; 邵广军; 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: 2021-09-14
Anticipated expiration: 2040-08-24
Also published as: CN112128350A

Abstract

The invention relates to the technical field of double-screw extruder gear boxes, and discloses a same-phase assembly adjusting method of a parallel and same-direction output structure, which comprises a box body, a first output shaft system, a transition 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, comparing and calculating the number of teeth and the axial movement required to adjust the rotation; s5, adjusting according to the calculation result in S4. The output same phase is adjusted according to the method of the invention, the internal structure of the existing gear box is not required to be modified, the torque transmission capacity of the gear pair is ensured, in addition, the adjustment is carried out according to the result obtained by accurate measurement and comparative calculation, repeated disassembly and reassembly are not required, the adjustment difficulty can be greatly reduced, the assembly and adjustment time is shortened, and manpower and material resources are greatly saved.

Description

Same-phase assembly adjustment method for parallel and same-direction output structure

Technical Field

The invention relates to the technical field of gear boxes of double-screw extruders, in particular to a same-phase assembly adjusting method of a parallel and same-direction 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 present invention provides an in-phase assembly adjustment method for parallel and unidirectional output structure to overcome some of the above-mentioned deficiencies in the prior art.

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

The same-phase assembly adjustment method of the parallel and same-direction output structure comprises a box body, a first output shaft system, a transition shaft system and a second output shaft system; 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, and an output end of the first output shaft is provided with an external spline E; the transition shaft system comprises a transition shaft rotationally connected to the box body, a gear B and a helical gear C which are fixed on the transition shaft; the second output shaft system comprises a second output shaft which is rotationally connected to the box body and a helical gear D fixed on the second output shaft, and the output end of the second output shaft is provided with an external spline F; the axes of the first output shaft, the transition shaft and the second output shaft are parallel to each other, and the gear A and the gearB, externally meshing, namely externally meshing the bevel gear C and the bevel gear D; the torque transmission direction is that the first output shaft transmits to the transition shaft, and the transition shaft transmits to the second output shaft; the first output shaft and the second output shaft have the same output direction and the same output rotating speed; the design positions of the end face of the external spline E and the end face of the external spline F are in the same plane, the phase design positions of the external spline E and the external spline F are in the same phase, and the number of teeth of the gear A is recorded as Z_AThe number of teeth of gear B is denoted as Z_BAnd the number of teeth of helical gear C is denoted as Z_CAnd the number of teeth of helical gear D is denoted as Z_DAnd the number of teeth of the external spline E is represented as Z_EAnd the number of teeth of the external spline F is represented as Z_F，Z_E=Z_FNumber of teeth Z of helical gear D_DNumber of teeth Z greater or less than external spline F_FThe method comprises the following steps:

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

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 a gear B and a bevel gear C in the assembled transition shaft system, and recording the angle error as phi by taking the gear B as the reference_C(ii) a Measuring the angular error of the helical gear D and the external spline F in the assembled second output shaft system, and recording the angular error as phi by taking the helical gear D as the reference_F；

Step S2, assembling the shafts on the box body, wherein the external spline E and the external spline F are assembled according to the designed positions, and the end surface of the external spline E and the end surface of the external spline F are positioned on the same plane;

step S3, calculating the error phi due to the angle_AThe angular deviation resulting from gear B is noted as θ_B，θ_B=-φ_A*（Z_A/Z_B) (ii) a Calculate the total angular deviation of the bevel gear C and record as θ_C，θ_C=θ_B+φ_C(ii) a Calculating the deviation theta due to the total angle_CThe angular deviation caused by the bevel 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+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_F；

Step S4, calculating the unit phase shift generated by the external spline F caused by each rotation of the helical gear D and recording the unit phase shift as delta_DF，Δ_DF=360/Z_D-360/Z_F(ii) a By gamma_{Regulating device}Divided by Δ_DFThe resulting integer quotient is denoted n and the resulting remainder is denoted gamma_SurplusAnd hold γ_SurplusAnd gamma_{Regulating device}The positive and negative are the same; comparison of gamma_SurplusSum of absolute values of_DFAbsolute value of/2 if γ_SurplusIs less than or equal to Δ_DFThe absolute value of/2, n is the number of teeth of the helical gear D which need to be adjusted and rotated, and gamma_SurplusI.e. calculating gamma for the remaining adjustment rotation angle_SurplusThe absolute value of the second output shaft is corresponding to the lead section length of the helical gear D, and the lead section length is the axial movement amount of the second output shaft and is marked as L_SurplusThe helical gear D will rotate inevitably when moving axially, this direction of rotation and the remaining adjustment rotation angle gamma_SurplusThe corresponding rotating directions are the same; if gamma is_SurplusIs greater than delta_DFThe absolute value of/2, n + n/| n | is calculated and the result is recorded as n_Super-superThen calculating gamma_{Regulating device}-Δ_DF*n_Super-superAnd the calculation result is recorded as gamma_Super-superThen n is_Super-superThe number of teeth, gamma, to be rotated for the bevel gear D needs to be adjusted_Super-superFor remaining adjustment of the rotation angle, gamma is calculated_Super-superThe absolute value of the second output shaft is corresponding to the lead section length of the helical gear D, and the lead section length is the axial movement amount of the second output shaft and is marked as L_Super-superThe helical gear D will rotate inevitably when moving axially, this direction of rotation and the remaining adjustment rotation angle gamma_Super-superThe corresponding rotating directions are the same;

step S5, keeping the phase position of the external spline E unchanged, if gamma is_SurplusIs less than or equal to Δ_DFThe absolute value of/2, the helical gear D is adjusted and rotated by n tooth positions and then is moved by the axial movement L_SurplusAxially moving the second output shaft, and ensuring the rotation direction of the helical gear D and the residual adjustment rotation angle gamma when axially moving the second output shaft_SurplusThe corresponding rotating directions are the same; if gamma is_SurplusIs greater than delta_DFAbsolute value of/2, the helical gear D is adjusted to rotate by n_Super-superTooth position and then according to the axial movement L_Super-superAxially moving the second output shaft, and ensuring the rotation direction of the helical gear D and the residual adjustment rotation angle gamma when axially moving the second output shaft_Super-superThe corresponding rotation directions are the same.

In the present embodiment, the casing body usually further includes other shafting and gears, such as an input shaft and a gear thereon, but the purpose of the present embodiment is to relate to structures of a rotating shaft, a gear, a spline and the like in the first output shafting, the transition 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 embodiment by referring 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 helical gear C are counterclockwise, and the rotation directions of the helical 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 bevel gear C in the assembled transition shaft system, taking the gear B as the reference, namely if the gear B is fixed and the error of the bevel gear C relative to the gear B is 0.2 degrees anticlockwise, then phi_C=0.2 degree, and phi is given when the error of the helical gear C with respect to the gear B is 0.2 degree clockwise_C=0.2 degrees; and measuring the angle error of the helical gear D and the external spline F in the assembled second output shafting, and taking the helical gear D as the reference, namely if the helical gear D is fixed and the error of the external spline F relative to the helical gear D is 0.15 degrees in a counterclockwise way, phi is measured_F=0.15 degrees, and if the error of the external spline F with respect to the helical gear D is 0.15 degrees clockwise, phi is_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 transition 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 assembling 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.

After calculating the total angular deviation theta of the external spline F_FThen, there are two options for adjusting the tooth position of the rotary helical gear D. For example, one is to adjust the tooth positions of the rotating bevel gear D by five tooth positions to leave a deviation theta from the total angle_FSmall angular phase deviation in the same direction, the remaining deviation theta from the total angle_FThe small-angle phase deviation in the same direction cannot be adjusted by adjusting the tooth position of the rotating helical gear D, and can only be adjusted by axially moving the helical gear D; the other is to adjust six tooth positions of the rotary helical gear D so that the actually adjusted total phase deviation is larger than the calculated total angle deviation theta_FBeyond a deviation from the total angle theta_FSmall angular phase deviation in the opposite direction, this remaining deviation from the total angle theta_FThe small angular phase deviation in the opposite direction cannot be adjusted by adjusting the tooth position of the rotating helical gear D, but can be adjusted only by axially moving the helical gear D, but the directions of the two axial movements are opposite, and the distances of the two axial movements are generally one large or one small. In step S4 of the method, the absolute values of the two small-angle phase deviations are compared, and the smaller distance that the helical gear D moves in the axial direction is smaller, so that the change of the meshing contact area between the helical gear D and the helical gear C is smaller, and the influence on the meshing effect between the gears and the torque transmission capability of the gear pair is smaller.

The total angular deviation theta of the external spline F calculated in the method_FI.e. the actual phase deviation of the external spline F relative to the external spline E. The method is characterized in that the positions of the external splines E and the external splines F which are adjusted to be in the same phase are realized by adjusting the rotating bevel gear D and axially moving the second output shaft, the end face of the external spline E and the end face of the external spline F are inevitably axially dislocated after the second output shaft is axially moved, but the axial dislocation amount is small, and a clearance sheet with the thickness equal to the axial movement amount is added between the end face of the external spline E and the end face of the screw rod or between the end face of the external spline F and the end face of the screw rod to compensate when the screw rod is connected. 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 bevel gear D is basically small when the same phase is adjusted according to the method, so that the meshing between the bevel gear D and the bevel gear C is realizedThe change of the engagement contact area is small, and the influence on the meshing effect between the gears, the torque transmission capacity of the gear pair and the like is small. More importantly, the same phase is adjusted according to the method, the internal structure of the existing gear box is not required to be modified, more connection or matching relation is not required to be added, the material and process cost cannot be improved, the torque transmission capacity of the gear pair is ensured, the low-speed extruder and the high-speed extruder are both suitable for use, in addition, the results obtained through accurate measurement and comparative calculation are adjusted according to the obtained results, so that the repeated disassembly and reassembly of various gear shafting or gears and the like are not required, the adjustment difficulty can be reduced, the assembly and adjustment time is shortened, and manpower and 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 bevel gear C and bevel gear D and recording as j_CDWhen the single-side circumferential backlash of the tooth profile of the helical gear C is offset based on the operating state and with the helical gear C as a reference, the backlash angle at which the helical gear D needs to rotate is expressed as μ_DThen μ_D=+/-（j_CD/dp_D) (180/pi); wherein dp_BIs the pitch diameter, dp, of gear B_DPitch diameter of bevel gear D, backlash angle mu_BAnd the backlash angle mu_DIs determined according to the method of claim 1;

the step S3 is: calculating the error phi due to the angle_AThe angular deviation resulting from gear B is noted as θ_B，θ_B=-φ_A*（Z_A/Z_B) (ii) a Calculate the total angular deviation of the bevel gear C and record as θ_C，θ_C=θ_B+μ_B+φ_C(ii) a Calculating the deviation theta due to the total angle_CThe angular deviation caused by the bevel 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_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 by accurate measurement and comparative calculation, so that each gear shaft system or gear and the like do not need to be repeatedly disassembled and assembled, 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 transition 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 gears and the external splines at the two output shafts and the transition shaft according to the first embodiment of the present invention, which are assembled in phase according to the design and then have an angular error.

Fig. 10 is a schematic diagram illustrating the phase change of the external spline F when the helical gear D rotates clockwise 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 transition shaft in the third embodiment of the present invention in a designed state without angular error.

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 gears and the external splines at the two output shafts and the transition shaft according to the third embodiment of the present invention in the state of angular error after the same phase assembly 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 clockwise 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, a transition 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 comprises a long output shaft 41 rotatably connected to the box body 1, and a bevel gear N42 and a bevel gear A43 which are fixed on the long output shaft 41, and the output end of the long output shaft 41 is provided with an external spline E44 which is integrally processed. The transition shaft system 5 comprises a transition shaft 51 which is rotationally connected with the box body 1, and a bevel gear B52 and a right-hand bevel gear C53 which are fixed on the transition shaft 51. The second output shaft system 6 comprises a short output shaft 61 rotationally connected to the box body 1 and a left-handed helical gear D62 fixed on the short output shaft 61, and the output end of the short output shaft 61 is provided with an external spline F63 which is integrally machined. The axes of the input shaft 21, the secondary rotating shaft 31, the long output shaft 41, the transition 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 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 second-stage rotating shaft 31, the second-stage rotating shaft 31 is transmitted to the long output shaft 41, the long output shaft 41 is transmitted to the transition shaft 51, and the transition 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. 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 transition 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 transition 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_AAnd the number of teeth of the helical gear D62 is represented as Z_D，Z_A=Z_D= 29. The number of teeth of helical gear B52 is denoted as Z_BAnd the number of teeth of the helical gear C53 is represented as Z_C，Z_B=Z_C= 55. 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, obviously Z_DGreater than Z_F。

The in-phase assembly adjustment method of the parallel and unidirectional output structure of the embodiment 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 transition 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. In the embodiment, the angular error value of the bevel gear A43 and the external spline E44 measured by the coordinate measuring machine is 1.2 degrees. As shown in FIG. 4, the angular error is recorded as φ from the external spline E44_AThat is, assuming that the external spline E44 is fixed (a series of oblique lines are drawn in the part of the external spline E44 in fig. 4 to indicate that the external spline E44 is fixed), the angular error of the helical gear a43 with respect to the external spline E44 is 1.2 degrees counterclockwise, phi_A=1.2 degrees.

When the transition shaft system 5 is assembled, the bevel gear B52 and the bevel gear C53 of the embodiment are fixedly connected with the transition shaft 51 through flat keys. As shown in FIG. 5, the design positions of the bevel gear B52 and the bevel gear C53 are that the symmetry line of the key slot, the symmetry line of one tooth profile of the bevel gear B52 and the symmetry line of one tooth profile of the bevel gear C53 are coincident and in a vertical position, and the key slot and the bevel gear are arranged in the vertical positionThe tooth profile of the wheel B52 and the tooth profile of the bevel gear C53 are both located above the axial center of the transition shaft 51. 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 B52 and the bevel gear C53. In the embodiment, the angular error values of the bevel gear B52 and the bevel gear C53 measured by the coordinate measuring machine are 1 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), the angular error of the helical gear C53 with respect to the helical gear B52 is 1 degree counterclockwise, phi_C=1 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 degree. 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 shown by a series of oblique lines to indicate that the helical gear D62 is assumed to be fixed), the error of the male spline F63 with respect to the helical gear D62 is 1 degree clockwise, φ_F=1 degree.

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.

Because 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 assembly process can be performed according to the designed in-phase position only by using the key groove as a reference, as shown in fig. 1 and 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_BAt the same time, the helical gear C53 also generates the same angular deviation with the helical gear B52. The transmission ratio i = omega of the first gear and the second gear which are mutually externally meshed_A/ω_II=Z_II/Z_AAnd ω is_A=Δθ_A/Δt_A，ω_II=Δθ_II/Δt_IIWherein ω is_AAngular velocity, omega, of gear one_IIIs the angular velocity, Z, of gear two_AIs the number of teeth of gear one, Z_IINumber of teeth of gear two, Δ θ_AFor gear one at delta t_AAngle of rotation in time, Δ θ_IIIs the second gear at delta t_IIThe angle of rotation in time. The time during which the first and second gears which mesh with each other rotate during operation is the same, i.e. Δ t_A=Δt_IIFrom which ω is derived_A/ω_II=（Δθ_A/Δt_A）/（Δθ_II/Δt_II）=Δθ_A/Δθ_II=Z_II/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_ABevel gear A43 and bevel gear B52 are externally meshed, and bevel gear A43 rotates by an angle phi_AThe bevel gear B52 will be driven 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_IIIn addition to Z_AInstead of Z in the derived formula_A，Z_BInstead of Z in the derived formula_IIIn 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=1.2 × 29/55= -0.6327 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_BThe gear is suitable for standard gears, modified gears with modification coefficients, gears with standard installation and gears with non-standard installation.

The total angular deviation of bevel gear C53 is calculated and recorded as θ_C，θ_C=θ_B+φ_C= (-0.6327) +1=0.3673 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= -0.3673 × 55/29= -0.6966 degrees.

The total angular deviation of the male spline F63 is calculated and recorded as θ_F，θ_F=θ_D+φ_F= (-0.6966) + (-1) = -1.6966 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_FThe actual phase deviation of the external spline E44 and the external spline F63 is 1.6966 degrees clockwise deviation of the external spline F63 relative to the external spline E44 due to errors of machining, assembling and the like.

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=1.6966 degrees.

Step S4, calculating the unit phase shift of the helical gear D62 caused by the external spline F63 per one tooth position and recording the unit phase shift as delta_DF，Δ_DF=360/Z_D-360/Z_F=360/29-360/28= -0.4433 degrees. Unit phase shift delta in the present invention_DFWhether the calculated result is positive or negative is determined by the self structure 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 unit phase shift delta is determined_DFWhether it is positive or negative is uniquely determined, unit 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 unit phase shift Δ_DFWhether the number is positive or negative means that the direction of the unit 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 that the unit phase shift delta is maintained_DFIs an angle value, but as an exception, the unit phase shift Δ_DFWhether it is positive or negative is determined by the structure. Unit 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. In addition, since the unit phase of the male spline F63 is shifted from itself when the rotary helical gear D62 is adjusted, even if there is an angular error between the helical gear D62 and the male spline F63 due to machining or the like, the angular error is generated for each timeThe phase of the male spline F63 is still shifted clockwise by 0.4433 degrees per counterclockwise adjustment of the rotational helical gear D62 by one tooth position, and conversely, the phase of the male spline F63 is still shifted counterclockwise by 0.4433 degrees per clockwise adjustment of the rotational helical gear D62 by one tooth position. Fig. 10 shows a front-rear comparison of the helical gear D62 rotated clockwise by one tooth position in the present embodiment, and the helical gear D62 and the external spline F63 rotated clockwise by one tooth position and the phase of the external spline F63 is shifted counterclockwise by 0.4433 degrees.

By gamma_{Regulating device}Divided by Δ_DFThe resulting integer quotient is denoted n and the resulting remainder is denoted gamma_SurplusAnd hold γ_SurplusAnd gamma_{Regulating device}Positive and negative being equal, i.e. gamma_{Regulating device}/Δ_DF= 1.6966/(-0.4433) = -3 and 0.3667, i.e. n = -3, gamma_Surplus=0.3667 degrees. Comparison of gamma_SurplusSum of absolute values of_DFThe magnitude of the absolute value of/2, for this embodiment, | γ |_Surplus∣=0.3667，∣Δ_DF(/ 2= | -0.4433/2 | = 0.22165). Is obviously gamma_SurplusIs greater than delta_DFThe absolute value of/2, n + n/| n | is calculated and the result is recorded as n_Super-super，n_Super-super= n + n/| n = (-3) + (-3)/| -3 | = -4. Then calculating gamma_{Regulating device}-Δ_DF*n_Super-superAnd the calculation result is recorded as gamma_Super-super，γ_Super-super=γ_{Regulating device}-Δ_DF*n_Super-super=1.6966- (-0.4433) × (-4) = -0.0766 degrees. Wherein n is_Super-superThe number of teeth of the helical gear D, which needs to be rotated, is a parameter related to the rotation direction, and the above-mentioned positive and negative values are also applied. For the present embodiment, n_Super-super=-4，n_Super-superIs a negative number, that is, four tooth positions of the rotating bevel gear D62 need to be adjusted clockwise. Gamma ray_Super-superThe residual adjustment rotation angle of the external spline F63 after four tooth positions of the rotating bevel gear D62 are adjusted clockwise, and the residual adjustment rotation angle gamma_Super-superIt is adjusted by axially moving the short output shaft 61 and the helical gear D62.

Calculating gamma_Super-superThe absolute value of (a) corresponds to the lead section length of the helical gear D62, which is the axial movement of the second output shaft and is marked as L_Super-super. Helical gearThe lead formula of (d) 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 helix 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_Super-superThe absolute value of (D) corresponds to the axial movement amount L of the helical gear D62_Super-super=L_D*（∣γ_Super-super∣/360）=2002.4975*（∣-0.0766∣/360）=0.4261mm。

The helical gear D62 will rotate inevitably when moving axially, and the rotation direction and the residual adjustment rotation angle gamma_Super-superThe corresponding rotation directions are the same. For the present embodiment, the remaining adjustment rotation angle γ_Super-super= 0.0766 degree, [ gamma ]_Super-superIs a negative number, and the corresponding rotation direction is clockwise, i.e. when moving the helical gear D62 axially, it is necessary to ensure that the helical gear D62 rotates clockwise. Helical gear C53 is a right-handed helical gear and helical gear D62 is a left-handed helical gear, and it is necessary to axially shift helical gear D62 to the right by 0.4261mm 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_Super-superThe corresponding rotation direction is determined.

Step S5, keeping the phase position of the external spline E44 unchanged, rotating the helical gear D62 clockwise by four tooth positions, and then moving the short output shaft 61 with the helical gear D62 and the external spline F63 rightward and axially by 0.4261 mm. After adjustment, the external spline F63 protrudes 0.4261mm to the right relative to the external spline E44, namely the external spline F63 is axially dislocated 0.4261mm to the right relative to the external spline E44, and when two screws of a twin-screw extruder are connected, a gap piece with the thickness of 0.4261mm can be added between the end face of the external spline E44 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 (| 1.6966 |/360) =9.4373 mm. That is, the short output shaft 61, the helical gear D62 and the external spline F63 need to be axially moved by 9.4373mm, 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 makes the axial displacement amount between the end surface of the external spline E44 and the end surface of the external spline F63 large, so that the short output shaft, the helical gear D62 and the external spline F63 cannot be supplemented by a gap piece.

And if gamma is not compared_SurplusSum of absolute values of_DFThe absolute value of/2, n is directly used as the number of teeth of the helical gear D which needs to be adjusted to rotate, and γ is used_SurplusAs the remaining adjustment rotation angle of the external spline F63, the remaining adjustment rotation angle γ is_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 (| 0.3667 |/360) =2.0398 mm. I.e. the short output shaft 61, the bevel gear D62 and the external spline F63, require 2.0398mm of axial movement, obviously L_SurplusGreater than L_Super-superMore specifically, the smaller the residual adjustment rotation angle, the smaller the axial movement amount, the smaller the influence of the smaller axial movement amount on the meshing contact surface, the meshing effect, the torque transmission capability of the gear pair, and the like, and the thinner the gap piece to be added, so that the effect obtained by selecting a smaller residual adjustment rotation angle for the corresponding in-phase adjustment is better.

In the embodiment, the external spline E44 and the external spline F63 are adjusted to be in the same phase position by adjusting the rotating bevel gear D62 and axially moving the short output shaft 61, and after the short output shaft 61 is axially moved, an axial offset is inevitably caused between 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 61, but the axial offset is relatively small, and a clearance piece with the same thickness as the axial movement is added between the end surface of the external spline E44 and the end surface of the screw rod when the screw rod is connected to compensate.

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 minimizes the amount of axial misalignment between the end face of the male spline E44 and the end face of the male spline F63. 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 gearbox of the twin-screw extruder as an example in the first embodiment, and the corresponding angle error measured in the first embodiment is used, and the relevant 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 engaged, is supplemented_B=770mm。

The in-phase assembly adjustment method of the parallel and equidirectional output structure according to the present embodiment is based on the first embodiment, in consideration that there is usually a backlash in the gear pair in the operating state, and this backlash can be regarded as an assembly error, so the method includes step S21 after step S2 in the first embodiment: 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. The circumferential 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. Based on the operating state and with the bevel gear A as the referenceThe backlash angle at which the helical gear B needs to rotate when the single-sided circumferential backlash of the tooth profile of the helical gear B is offset 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 of 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 circumferential backlash j is cancelled_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: calculating due to external flowerAngular error phi of key E44 and helical gear A43_AThe angular deviation resulting in bevel gear B52 is noted as θ_B，θ_B=-φ_AZ_A/Z_BAnd the angular deviation of the helical gear C53 is the same as that of the helical gear B52 while the angular deviation of the helical gear C is-1.2 × 29/55= -0.6327 degrees.

The total angular deviation of bevel gear C53 is calculated and recorded as θ_C，θ_C=θ_B+μ_B+φ_C= (-0.6327) + (-0.0409) +1=0.3264 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 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= -0.3264 × 55/29= -0.619 degrees.

The total angular deviation of the male spline F63 is calculated and recorded as θ_F，θ_F=θ_D+μ_D+φ_FAnd (= (-0.619) +0.079+ (-1) = -1.54 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_CCausing helical gear D62 and male spline F63 to rotate together by an 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_FOutside, inTotal angular deviation θ of spline F63_FNamely, the actual phase deviation of the external spline E44 and the external spline F63, namely, the external spline F63 in the present embodiment is deviated by 1.54 degrees clockwise relative to the external spline E44 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=1.54 degrees.

Step S4, calculating the unit phase shift of the helical gear D62 caused by the external spline F63 per one tooth position and recording the unit phase shift as delta_DF，Δ_DF=360/Z_D-360/Z_F=360/29-360/28= -0.4433 degrees.

By gamma_{Regulating device}Divided by Δ_DFThe resulting integer quotient is denoted n and the resulting remainder is denoted gamma_SurplusAnd hold γ_SurplusAnd gamma_{Regulating device}Positive and negative being equal, i.e. gamma_{Regulating device}/Δ_DF= 1.54/(-0.4433) = -3, i.e. n = -3, y 0.2101_Surplus=0.2101 degrees. Comparison of gamma_SurplusSum of absolute values of_DFThe magnitude of the absolute value of/2, for this embodiment, | γ |_Surplus∣=0.2101，∣Δ_DF(/ 2= | -0.4433/2 | = 0.22165). Is obviously gamma_SurplusIs less than delta_DFThe absolute value of/2, n is the number of teeth of the helical gear D that need to be rotated, n is a parameter related to the direction of rotation, and the same applies to the above-mentioned positive and negative values. For the present embodiment, n = -3, where n is a negative number, that is, three tooth positions of the rotating helical gear D62 need to be adjusted clockwise first. Gamma ray_SurplusThe residual adjustment rotation angle of the external spline F63 after the clockwise adjustment of the three tooth positions of the rotating bevel gear D62 is shown as gamma_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=2002.4975mm, remaining adjustment rotation angleDegree 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*（∣0.2101∣/360）=1.1687mm。

When the bevel gear D62 is moved axially for adjustment, the bevel gear D62 will inevitably rotate, and the rotation direction and the remaining adjustment rotation angle γ_SurplusThe corresponding rotation directions are the same. For the present embodiment, the remaining adjustment rotation angle γ_Surplus0.2101 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 1.1687mm 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 three tooth positions, and then axially moving the short output shaft 61 with the helical gear D62 and the external spline F63 leftward by 1.1687mm as shown in fig. 1. After adjustment, the external spline F63 is retracted 1.1687mm leftwards relative to the external spline E44, namely the external spline F63 is axially dislocated 1.1687mm 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 1.1687mm 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 adjusting the in-phase assembly of the parallel and equidirectional output structure according to the present embodiment has the advantages of the first embodiment, and in addition, the backlash is taken into consideration, that is, the adjustment is performed based on the operating state, so that it is ensured that the in-phase output by the male spline E44 and the male spline F63 in the operating state 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, a transition 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 shaft system 8 comprises a long output shaft 81 rotatably connected to the box body, and a bevel gear T82 and a bevel gear A83 which are fixed on the long output shaft 81, and the output end of the long output shaft 81 is provided with an external spline E84 which is integrally processed. The transition shaft system 9 comprises a transition 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 transition shaft 91. The second output shaft system 10 comprises a short output shaft 101 rotatably connected to the box body and a right-handed helical gear D102 fixed on the short output shaft 101, and an external spline F103 integrally formed is arranged at the output end of the short output shaft 101. The axial centers of the input shaft 71, the long output shaft 81, the transition shaft 91 and the short output shaft 101 are parallel to each other, the helical gear S72 is externally engaged with the helical gear T82, the helical gear A83 is externally engaged with the helical gear B92, and the helical gear C93 is externally engaged 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 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 transmission direction in this gear box is that the input shaft 71 is transmitted to the long output shaft 81, the long output shaft 81 is transmitted to the transition shaft 91, and the transition shaft 91 is transmitted to the 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 transition 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 transition 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. Is very clear of Z_DLess than Z_F. 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 transition 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 a fixed male spline E84 (a series of oblique lines are drawn in the portion of the male spline E84 in fig. 16 to indicate the assumed fixed male spline E84), the angular error of the helical gear a83 with respect to the male spline E84 is counterclockwise0.48 degree, then phi_A=0.48 degrees.

When the transition shaft system 9 is assembled, the bevel gear B92 and the bevel gear C93 of the embodiment are fixedly connected with the transition shaft 91 through flat keys. As shown in fig. 17, the design positions of the helical gear B92 and the helical gear C93 are the symmetry line of the key slot, the symmetry line between the two tooth profiles of the helical gear B92 and the symmetry line of one tooth profile of the helical gear C93 are coincident and in a vertical position, and the key slot, the two tooth profiles of the helical gear B92 and the tooth profile of the helical gear C93 are all located above the axial center of the transition 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 0.25 degrees. 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 0.25 degrees clockwise, and then Φ is set to be phi_C=0.25 degrees.

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. The invention is based on the consideration of the operation state, and only needs to consider the tooth profile single-side 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_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. For the present embodiment, the positive and negative values are determined as described aboveIn view of the above, as shown in FIG. 22, assuming that the helical gear A83 is fixed, the circumferential backlash j is offset by using the helical gear A83 as a reference, that is, the helical gear A83 as a counterclockwise driving wheel based on the driving state_ABThen helical gear B92 would need to rotate counterclockwise, i.e., the backlash angle μ at which helical gear B92 would need 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+ (-0.25) = -0.4233. 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_AResulting in skewed teethThe wheel B92 and the bevel gear C93 rotate together by an angle theta_BThen keeping bevel gear A83 still, bevel gear B92 and bevel gear C93 rotate together by an angle mu_BThen holding bevel gear B92 stationary, as does external spline E84, and bevel gear C93 rotated an angle φ_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= 0.4233 × 52/24=0.9172 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=0.9172+ (-0.1194) +0.31=1.1078 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 1.1078 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= -1.1078 degrees.

In step S4, the unit phase shift of the external spline F103 caused by each rotation of the helical gear D102 is calculated andis recorded as Delta_DF，Δ_DF=360/Z_D-360/Z_F=360/24-360/25=15-14.4=0.6 degrees. Unit phase shift Δ of the present embodiment_DFIs a positive number, which indicates that the phase of the external spline F103 is shifted counterclockwise by 0.6 degrees every time the helical gear D102 is rotated counterclockwise by one tooth position; 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 clockwise by one tooth position, and the helical gear D102 and the external spline F103 are rotated clockwise by one tooth position, and then the phase of the external spline F103 is shifted clockwise by 0.6 degrees.

By gamma_{Regulating device}Divided by Δ_DFThe resulting integer quotient is denoted n and the resulting remainder is denoted gamma_SurplusAnd hold γ_SurplusAnd gamma_{Regulating device}Positive and negative being equal, i.e. gamma_{Regulating device}/Δ_DF= 1.1078/0.6= -1 or more-0.5078, i.e. n = -1, γ_Surplus= -0.5078 degrees. Comparison of gamma_SurplusSum of absolute values of_DFThe magnitude of the absolute value of/2, for this embodiment, | γ |_Surplus∣=0.5078，∣Δ_DF(/ 2= |) 0.6/2 | = 0.3. Is obviously gamma_SurplusIs greater than delta_DFThe absolute value of/2, n + n/| n | is calculated and the result is recorded as n_Super-super，n_Super-super= n + n/| n = (-1) + (-1)/| -1 | = -2. Then calculating gamma_{Regulating device}-Δ_DF*n_Super-superAnd the calculation result is recorded as gamma_Super-super，γ_Super-super=γ_{Regulating device}-Δ_DF*n_Super-superAnd (= -1.1078-0.6 x (-2) =0.0922 degrees. Wherein n is_Super-superThe number of teeth of the helical gear D, which needs to be rotated, is a parameter related to the rotation direction, and the above-mentioned positive and negative values are also applied. For the present embodiment, n_Super-super=-2，n_Super-superIs a negative number, that is, it needs to adjust two tooth positions of the rotating bevel gear D102 clockwise first. Gamma ray_Super-superThe residual adjustment rotation angle of the external spline F103 after clockwise adjusting two tooth positions of the rotating helical gear D102 is gamma_Super-superIt is adjusted by axially moving the short output shaft 101 and the helical gear D102.

Calculating gamma_Super-superIs absoluteThe value of the lead section length of the helical gear D102 corresponds to, the lead section length is the axial movement amount of the second output shaft and is marked as L_Super-super. Lead L of helical gear D102_D=π*dp_D/tanβ_D= pi 120/tan9=2380.2282 mm. Residual adjustment rotation angle gamma_Super-superThe axial movement amount L of the helical gear D102 corresponding to the absolute value of (A)_Super-super=L_D*（∣γ_Super-super∣/360）=2380.2282*（0.0922/360）=0.6096mm。

The helical gear D102 will rotate inevitably when moving axially, and this rotation direction and the remaining adjustment rotation angle gamma_Super-superThe corresponding rotation directions are the same. For the present embodiment, the remaining adjustment rotation angle γ_Super-super=0.0922 degree,. gamma_Super-superIs a positive number, and the corresponding rotation direction is counterclockwise, i.e. it is necessary to ensure that the helical gear D102 rotates counterclockwise when the helical gear D102 is moved axially. Helical gear C93 is the left hand helical gear and helical gear D102 is the right hand helical gear, and it is necessary to move helical gear D102 to the right by 0.6096mm as shown in FIG. 13. That is, the axial moving direction of the helical gear D102 is based on the helical direction of the helical gear C93 and the helical gear D102 and the remaining adjustment rotation angle γ_Super-superThe corresponding rotation direction is determined.

Step S5, keeping the phase position of the external spline E84 unchanged, rotates the helical gear D102 clockwise by two tooth positions, and then moves the short output shaft 101 with the helical gear D102 and the external spline F103 to the right by 0.6096mm in the axial direction. After adjustment, the external spline F103 protrudes 0.6096mm rightwards relative to the external spline E84, namely the external spline F103 is axially displaced 0.6096mm rightwards relative to the external spline E84, and when two screws of a twin-screw extrusion granulator are connected, a gap sheet with the thickness of 0.6096mm can be added between the end face of the external spline E84 and the screws so as to offset the axial displacement between the external spline E84 and the external 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 (| 1.1078 |/360) =7.3245 mm. That is, the short output shaft 101 and the helical gear D102 need to be axially moved by 7.3245mm, 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.

And if gamma is not compared_SurplusSum of absolute values of_DFThe absolute value of/2, n is directly used as the number of teeth of the helical gear D which needs to be adjusted to rotate, and γ is used_SurplusAs the remaining adjustment rotation angle of the external spline F103, then the remaining adjustment rotation angle γ_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 (| 0.5078 |/360) =3.3574 mm. I.e. the short output shaft 101, the bevel gear D102 and the external spline F103 need to be axially displaced 3.3574mm, obviously L_SurplusGreater than L_Super-superMore specifically, the smaller the residual adjustment rotation angle, the smaller the axial movement amount, the smaller the influence of the smaller axial movement amount on the meshing contact surface, the meshing effect, the torque transmission capability of the gear pair, and the like, and the thinner the gap piece to be added, so that the effect obtained by selecting a smaller residual adjustment rotation angle for the corresponding in-phase adjustment is better.

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 caused between the end face of the external spline E84 and the end face of the external spline F103, but the axial misalignment is relatively small, and a clearance piece with the same thickness as the axial movement is added between the end face of the external spline E84 and the end face of the screw rod when the screw rod is connected to compensate.

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 can minimize the amount of axial misalignment between the end face of the male spline E84 and the end face of the male spline F103. 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 accurate measurement and comparative calculation, adjust according to the result that draws can, 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 same-phase assembly adjustment method of the parallel and same-direction output structure comprises a box body, a first output shaft system, a transition shaft system and a second output shaft system; 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, and an output end of the first output shaft is provided with an external spline E; the transition shaft system comprises a transition shaft rotationally connected to the box body, a gear B and a helical gear C which are fixed on the transition shaft; the second output shaft system comprises a second output shaft which is rotationally connected to the box body and a helical gear D fixed on the second output shaft, and the output end of the second output shaft is provided with an external spline F; the axes of the first output shaft, the transition shaft and the second output shaft are parallel to each other, the gear A is externally meshed with the gear B, and the helical gear C is externally meshed with the helical gear D(ii) a The torque transmission direction is that the first output shaft transmits to the transition shaft, and the transition shaft transmits to the second output shaft; the first output shaft and the second output shaft have the same output direction and the same output rotating speed; the design positions of the end face of the external spline E and the end face of the external spline F are in the same plane, the phase design positions of the external spline E and the external spline F are in the same phase, and the number of teeth of the gear A is recorded as Z_AThe number of teeth of gear B is denoted as Z_BAnd the number of teeth of helical gear C is denoted as Z_CAnd the number of teeth of helical gear D is denoted as Z_DAnd the number of teeth of the external spline E is represented as Z_EAnd the number of teeth of the external spline F is represented as Z_F，Z_E=Z_FCharacterized in that the number of teeth Z of the helical gear D_DNumber of teeth Z greater or less than external spline F_FThe method comprises the following steps:

Step S4, calculating the unit phase shift generated by the external spline F caused by each rotation of the helical gear D and recording the unit phase shift as delta_DF，Δ_DF=360/Z_D-360/Z_F(ii) a By gamma_{Regulating device}Divided by Δ_DFThe resulting integer quotient is denoted n and the resulting remainder is denoted gamma_SurplusAnd hold γ_SurplusAnd gamma_{Regulating device}The positive and negative are the same; comparison of gamma_SurplusSum of absolute values of_DFAbsolute value of/2 if γ_SurplusIs less than or equal to Δ_DFThe absolute value of/2, n is the number of teeth of the helical gear D which need to be adjusted and rotated, and gamma_SurplusI.e. calculating gamma for the remaining adjustment rotation angle_SurplusThe absolute value of the second output shaft is corresponding to the lead section length of the helical gear D, and the lead section length is the axial movement amount of the second output shaft and is marked as L_SurplusLead L of helical gear D_D=π*dp_D/tanβ_DWherein dp_DIs the pitch diameter, beta, of the bevel gear D_DThe helical angle and the axial movement L of the helical gear D_Surplus=L_D*（∣γ_Surplus| 360), the helical gear D is inevitably rotated during its axial movement, this direction of rotation and the remaining adjustment rotation angle γ_SurplusThe corresponding rotating directions are the same; if gamma is_SurplusIs greater than delta_DFThe absolute value of/2, n + n/| n | is calculated and the result is recorded as n_Super-superThen calculating gamma_{Regulating device}-Δ_DF*n_Super-superAnd the calculation result is recorded as gamma_Super-superThen n is_Super-superThe number of teeth, gamma, to be rotated for the bevel gear D needs to be adjusted_Super-superFor remaining adjustment of the rotation angle, gamma is calculated_Super-superThe absolute value of the second output shaft is corresponding to the lead section length of the helical gear D, and the lead section length is the axial movement amount of the second output shaft and is marked as L_Super-superAmount of axial movement L_Super-super=L_D*（∣γ_Super-super| 360), the helical gear D is inevitably rotated during its axial movement, this direction of rotation and the remaining adjustment rotation angle γ_Super-superThe corresponding rotating directions are the same;

2. A method for adjusting an in-phase assembly of a parallel and equidirectional output structure as set forth in claim 1, wherein said step S2 is followed by a step S21 of measuring a circumferential backlash between the gear a and the gear B and denoted by 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 bevel gear C and bevel gear D and recording as j_CDWhen the single-side circumferential backlash of the tooth profile of the helical gear C is offset based on the operating state and with the helical gear C as a reference, the backlash angle at which the helical gear D needs to rotate is expressed as μ_DThen μ_D=+/-（j_CD/dp_D) (180/pi); wherein dp_BIs the pitch diameter, dp, of gear B_DPitch diameter of bevel gear D, backlash angle mu_BAnd the backlash angle mu_DIs determined according to the method of claim 1;