CN112364551B - Fatigue analysis method for planetary transmission gearbox - Google Patents
Fatigue analysis method for planetary transmission gearbox Download PDFInfo
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Abstract
The invention discloses a fatigue analysis method for a planetary transmission gearbox, which comprises the following steps: determining the rotation range of the meshing position according to the number of planet wheels in the gearbox, determining a plurality of different target meshing positions in the rotation range, and calculating the stress result of the gearbox corresponding to the target meshing positions; establishing a function for interpolation for the position angle of each target meshing position, so that the function can cover two angle positions adjacent to the current angle position, and obtaining a position proportionality coefficient-angle curve; calculating an angle-time sequence of each target engagement position; calculating a position load proportion coefficient-time sequence; and calculating a position load proportional coefficient-time sequence under each working condition, and calculating a fatigue result of the gearbox through fatigue software. The analysis method provided by the invention considers the additional dynamic characteristics caused by the rotation of the planetary system, not only can consider the change of the input load, but also can consider the influence of the change of the gear meshing position on the box body, and the analysis result is accurate and reliable.
Description
Technical Field
The invention relates to the field of gearbox fatigue analysis methods, in particular to a planetary transmission gearbox fatigue analysis method.
Background
The planet-stage gear transmission mode is widely applied to various fields of the mechanical industry, a planet carrier is used as an important part of planet transmission, and the structural design of the planet carrier not only needs to consider the requirement of torque transmission, but also needs to consider whether the static strength and the fatigue strength meet the design requirement.
The box body of the wind power gear box adopting a planetary gear transmission mode is used as a key force transmission part to bear complex dynamic load, and fatigue strength needs to be evaluated besides ultimate strength checking. At present, fatigue calculation of a box body is generally carried out by applying single torque on an inner gear ring connected with the box body or applying meshing force of a planet gear and the gear ring at a certain fixed position, calculating unit load stress and checking fatigue strength based on the unit load stress. In actual operation, along with the rotation of the planet carrier, the meshing position of the planet wheel and the inner gear ring is constantly changed, so the stress state of the box body is influenced by the gear meshing force position besides the change of the input load, the influence of the load on a single selected position is only considered in the conventional calculation mode, the weak point in the box body structure cannot be accurately covered and evaluated, and the safety risk exists.
Therefore, how to effectively improve the fatigue analysis accuracy of the planetary transmission gearbox is a technical problem to be solved by the technical personnel in the field at present.
Disclosure of Invention
The invention aims to provide a fatigue analysis method for a planetary transmission gearbox, which is used for accurately evaluating the fatigue reliability of the planetary transmission gearbox in the rotation process of a planetary system.
In order to achieve the purpose, the invention provides the following technical scheme:
a fatigue analysis method for a planetary transmission gearbox comprises the following steps:
step S1: determining the rotation range of the meshing position according to the number of planet wheels in the gearbox, determining a plurality of different target meshing positions in the rotation range, and calculating the stress result of the gearbox corresponding to the target meshing positions;
step S2: establishing a function for interpolation for the position angle of each target meshing position, so that the function can cover two angle positions adjacent to the current angle position, and obtaining a position proportionality coefficient-angle curve;
and step S3: calculating an angle-time sequence of each target meshing position according to the rotating speed-time sequence of the gearbox;
and step S4: calculating a position load proportionality coefficient-time series from the position proportionality coefficient-angle curve, the angle-time series, and the torque-time series of the gearbox;
step S5: and calculating a position load proportional coefficient-time sequence under each working condition, and calculating a fatigue result of the gearbox through fatigue software.
Preferably, the step S4 includes:
step S4-1: calculating to obtain a position proportionality coefficient-time sequence through the position proportionality coefficient-angle curve and the angle-time sequence;
step S4-2: calculating a load proportionality coefficient-time sequence through a torque-time sequence of the gearbox;
step S4-3: and calculating to obtain a position load proportion coefficient-time sequence through the position proportion coefficient-time sequence and the load proportion coefficient-time sequence.
Preferably, the step S2 further includes: and determining that the proportionality coefficient of the current angle position is 1 and the proportionality coefficients of the front and the back adjacent angle positions are 0.
Preferably, the step S1 includes:
modeling is carried out on the planetary transmission gearbox by utilizing transmission system analysis software, and a solid model extraction node and a rigidity matrix of the planetary transmission gearbox are led into the transmission system analysis software by combining finite element software, wherein the node is used for connecting components on a planet carrier of the gearbox.
Preferably, the step S1 further includes:
and calculating the model of the planetary transmission gearbox in the transmission system software, and calculating the stress result of the gearbox at each target meshing position.
Preferably, the step S1 includes:
establishing finite element models of a gearbox body and a gear ring, wherein the load boundary condition is divided into 5 load steps, the first 4 load steps respectively calculate the position of the gearbox body which rotates by 30 degrees at each meshing position in a 120-degree period under the nominal input torque, apply the meshing force of a planet wheel and an inner gear ring to the gear ring, and calculate to obtain 4 groups of stress results; calculating a stress result of the box body under the action of gravity in the 5 th loading step; 5 sets of finite element stress results were obtained.
Preferably, the step S2 includes:
establishing a position proportionality coefficient-angle curve of the first 4 groups of load steps and the related engagement positions, which is concretely as follows:
position proportionality coefficient-angle curve equation under 0 degree position
Position proportionality coefficient-angle curve equation under 30 deg. position
Position proportionality coefficient-angle curve equation under 60 deg. position
Position proportionality coefficient-angle curve equation under 90 deg. position
Preferably, the step S3 includes:
according to the rotating speed-time sequence of the gearbox, setting an initial angle to be 0 degrees, wherein the angle of each time point is equal to the time interval between the current time point and the previous time point, multiplying the rotating speed of the previous time point by the angle of the previous time point, and then adding the angle of the previous time point; and analogizing to obtain the angle of each time point, and then taking the remainder of the angle of each time point to 120 degrees so that the value of each angle does not exceed 120 degrees, thereby obtaining the angle-time sequence.
Preferably, the step S4 includes:
step S4-1: respectively substituting the angle-time sequences obtained in the step S3 into 4 sets of equations established in the step S2, and calculating to obtain 4 sets of position proportionality coefficients-time sequences;
step S4-2: according to the torque-time sequence of the gearbox, dividing the torque of each time point by the nominal torque used when the stress result is calculated in the step S1 to obtain a load proportionality coefficient-time sequence;
step S4-3: multiplying the 4 sets of position proportionality coefficient-time sequences obtained in the step S4-1 by the load proportionality coefficient-time sequences obtained in the step S4-2 respectively to obtain 4 sets of position load proportionality coefficient-time sequences related to the load size and the meshing position; because the magnitude and the direction of gravity are always unchanged, a group of gravity-time sequences with the proportionality coefficient of 1 are obtained; 5 sets of position load proportionality coefficient-time series were obtained.
Preferably, the step S5 includes:
and repeating the step S3 and the step S4 for all time sequence loads, inputting the obtained position load proportion coefficient-time sequence and the 5 groups of finite element stress results calculated in the step S1 into fatigue calculation software, and calculating the fatigue life and the fatigue damage of the gearbox by combining the S-N curve of the material and the cycle number of each time sequence load.
The invention provides a fatigue analysis method for a planetary transmission gearbox, which comprises the following steps: step S1: determining the rotation range of the meshing position according to the number of planet wheels in the gearbox, determining a plurality of different target meshing positions in the rotation range, and calculating the stress result of the gearbox corresponding to the target meshing positions; step S2: establishing a function for interpolation for the position angle of each target meshing position, so that the function can cover two angle positions adjacent to the current angle position, and obtaining a position proportionality coefficient-angle curve; and step S3: calculating an angle-time sequence of each target meshing position according to the rotating speed-time sequence of the gearbox; and step S4: calculating a position load proportionality coefficient-time series from the position proportionality coefficient-angle curve, the angle-time series and the torque-time series of the gearbox; step S5: and calculating a position load proportional coefficient-time sequence under each working condition, and calculating a fatigue result of the gearbox through fatigue software. The fatigue analysis method for the planetary transmission gearbox, provided by the invention, considers the additional dynamic characteristics caused by the rotation of the planetary system, not only can consider the change of the input load, but also can consider the influence of the change of the meshing position of the gear on the gearbox body, and the analysis result is accurate and reliable.
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In order to more clearly illustrate the embodiments of the present invention or the technical solutions in the prior art, the drawings used in the description of the embodiments or the prior art will be briefly described below, it is obvious that the drawings in the following description are only some embodiments of the present invention, and for those skilled in the art, other drawings can be obtained according to the drawings without creative efforts.
FIG. 1 is a flow chart of one embodiment of a method for analyzing fatigue of a planetary transmission gearbox according to the present invention;
FIG. 2 is a flow chart of another embodiment of the fatigue analysis method for the planetary transmission gearbox provided by the invention.
Detailed Description
The core of the invention is to provide a fatigue analysis method for a planetary transmission gearbox, which is used for accurately evaluating the fatigue reliability of the planetary transmission gearbox in the rotation process of a planetary system.
In order that those skilled in the art will better understand the disclosure, the invention will be described in further detail with reference to the accompanying drawings and specific embodiments.
Referring to fig. 1 and 2, fig. 1 is a flow chart of an embodiment of a fatigue analysis method for a planetary transmission gearbox according to the present invention; FIG. 2 is a flow chart of another specific embodiment of the fatigue analysis method for the planetary transmission gearbox provided by the invention.
In this embodiment, the planetary drive gearbox fatigue analysis method comprises the steps of:
step S1: determining the rotation range of the meshing position according to the number of planet wheels in the gearbox, determining a plurality of different target meshing positions in the rotation range, and calculating the stress result of the gearbox corresponding to the target meshing positions; specifically, the determination of the target meshing position can be set according to the type of the planetary gearbox;
step S2: establishing a function for interpolation for the position angle of each target meshing position, so that the function can cover two angle positions adjacent to the current angle position, and a position proportionality coefficient-angle curve is obtained;
and step S3: calculating an angle-time sequence of each target meshing position according to the rotating speed-time sequence of the gearbox;
and step S4: calculating a position load proportionality coefficient-time series from the position proportionality coefficient-angle curve, the angle-time series, and the torque-time series of the gearbox;
step S5: and calculating a position load proportional coefficient-time sequence under each working condition, and calculating a fatigue result of the gearbox through fatigue software.
The fatigue analysis method for the planetary transmission gearbox, provided by the invention, considers the additional dynamic characteristic caused by the rotation of the planetary system, not only can consider the change of the input load, but also can consider the influence of the change of the meshing position of the gears on the gearbox body, and the analysis result is accurate and reliable.
In addition to the above embodiments, the step S4 includes:
step S4-1: calculating to obtain a position proportionality coefficient-time sequence through the position proportionality coefficient-angle curve and the angle-time sequence;
step S4-2: calculating a load proportionality coefficient-time sequence through the torque-time sequence of the gearbox;
step S4-3: and calculating to obtain the position load proportion coefficient-time sequence according to the position proportion coefficient-time sequence and the load proportion coefficient-time sequence.
In addition to the above embodiments, the step S2 further includes: and determining that the proportionality coefficient of the current angle position is 1 and the proportionality coefficients of the front and the back adjacent angle positions are 0.
In addition to the above embodiments, the step S1 includes:
modeling is carried out on the planetary transmission gearbox by utilizing transmission system analysis software, and a solid model extraction node and a rigidity matrix of the planetary transmission gearbox are led into the transmission system analysis software by combining finite element software, wherein the node is used for connecting components on a planet carrier of the gearbox. The model is then calculated in the drive train software to obtain the reaction force on the gearbox planet carrier assembly.
Further, guiding the extracted rigidity model of the planet carrier of the gear box in the step S1 and the calculated reaction force into finite element analysis software, and carrying out static strength analysis on the finite element analysis software; the boundary conditions of the static strength analysis are limit load and gravity, due to the symmetry of the planet carrier, taking a 3-split planet carrier as an example, the gravity comprises four rotation positions of 0 degree, 30 degrees, 60 degrees and 90 degrees, stress or strain of 4 positions is obtained, the relation between the magnitude of the stress or strain and the rotation positions can be obtained through an interpolation method, the position with the maximum stress or strain is found out and used as a static strength analysis result, based on the result, the topology optimization is carried out on the planet carrier structure, the structure can meet the rigidity requirement and the lightweight design requirement, and in order to obtain an accurate and convergent result, the submodel analysis is carried out on the structure.
Furthermore, when fatigue strength analysis is carried out, finite element analysis is firstly carried out on a planet carrier of the gear box, stress or strain under the boundary condition of rated load is extracted, the load of the planet carrier is divided into 4 subsections in total, the subsections comprise simulated interference fit through friction contact, gravity of a planet carrier component, gravity of the planet carrier after rotating for 90 degrees (simulated rotation is carried out by forming an included angle of 90 degrees with the gravity of the previous step), and the rated load, and 4 groups of stress or strain are obtained after analysis.
In addition to the above embodiments, the step S1 further includes:
and calculating the model of the planetary transmission gearbox in the transmission system software, and calculating the acting force result of the gearbox at each target meshing position.
Further, the processing procedure of the position load proportionality coefficient-time series is as follows:
in the strength analysis of the planet carrier, because the stress generated by interference fit is unchanged, a group of load proportionality coefficients-time sequences with the load coefficient of 1 are added to the time sequence load; the gravity load simulates effective gravity in a rotating state by combining sine waves and cosine waves, and is zoomed as a function of the angle of the planet carrier; converting the rotating speed into an angular speed in the time sequence, calculating the time sequence by adopting a numerical integration method of the angular speed to time, and solving the angle of the planet carrier; the sine and cosine of this angle define the scale factor of the gravitational load; dividing the load in the time sequence by the rated load to obtain a load scale factor-time sequence, namely a load scale factor-time sequence; 4 groups of load proportion coefficient-time sequences are obtained; applying all the obtained load proportion coefficient-time sequences to all time sequence loads to obtain position load proportion coefficient-time sequences; and acquiring an SN (stress-element) or EN (element) curve according to the material attribute of the gearbox planet carrier, introducing 4 groups of stress or strain obtained by fatigue analysis and all obtained load proportionality coefficients-time sequences into fatigue analysis software, and carrying out fatigue analysis on the gearbox planet carrier to obtain the fatigue life and damage of the gearbox planet carrier.
In one embodiment, a gearbox case fatigue analysis method is described, taking a 3-split planetary system as an example. For a 3-split planetary system, the stress state change period of a box body is 120 degrees, 4 positions with equal intervals are taken in the period, the unit load stress of the gearbox body when the meshing positions of a planetary gear and an inner gear ring are at 0 degree (120 degrees, 240 degrees), 30 degrees (150 degrees, 270 degrees), 60 degrees (180 degrees, 300 degrees) and 90 degrees (210 degrees and 330 degrees) is respectively calculated, and the stress between two adjacent angles is obtained through linear interpolation; and performing multi-working-condition combined stress fatigue calculation in fatigue calculation software by combining the obtained stress result with the input load and the S-N curve of the material to obtain the fatigue life and the fatigue damage. Specifically, the step S1 includes:
establishing finite element models of a gearbox body and a gear ring, wherein the load boundary condition is divided into 5 load steps, the first 4 load steps respectively calculate the position of the gearbox body which rotates by 30 degrees at each meshing position in a 120-degree period under the nominal input torque, apply the meshing force of a planet wheel and an inner gear ring to the gear ring, and calculate to obtain 4 groups of stress results; the 5 th loading step is used for calculating a stress result of the box body under the action of gravity; 5 sets of finite element stress results were obtained.
Further, the step S2 includes:
establishing a position proportionality coefficient-angle curve of the first 4 groups of load steps and the related engagement positions, which is concretely as follows:
position proportionality coefficient-angle curve equation under 0 degree position
Position proportionality coefficient-angle curve equation under 30 deg. position
Position proportionality coefficient-angle curve equation under 60 deg. position
Position proportionality coefficient-angle curve equation under 90 deg. position
Further, the step S3 includes:
according to the rotating speed-time sequence of the gearbox, setting an initial angle to be 0 degrees, and multiplying the angle of each time point by the time interval between the current time point and the previous time point and then adding the angle of the previous time point; and analogizing to obtain the angle of each time point, and then taking the remainder of the angle of each time point to 120 degrees so that the value of each angle does not exceed 120 degrees, thereby obtaining the angle-time sequence.
Specifically, the step S4 includes:
step S4-1: respectively substituting the angle-time sequences obtained in the step S3 into 4 sets of equations established in the step S2, and calculating to obtain 4 sets of position proportionality coefficients-time sequences;
step S4-2: according to the torque-time sequence of the gearbox, dividing the torque of each time point by the nominal torque used when the stress result is calculated in the step S1 to obtain a load proportionality coefficient-time sequence;
step S4-3: multiplying the 4 sets of position proportionality coefficient-time sequences obtained in the step S4-1 by the load proportionality coefficient-time sequences obtained in the step S4-2 respectively to obtain 4 sets of position load proportionality coefficient-time sequences related to the load size and the meshing position; because the magnitude and the direction of gravity are always unchanged, a group of gravity-time sequences with the proportionality coefficient of 1 are obtained; 5 sets of position load proportionality coefficient-time series were obtained.
Further, the step S5 includes:
and repeating the step S3 and the step S4 for all time sequence loads, inputting the obtained position load proportion coefficient-time sequence and the 5 groups of finite element stress results calculated in the step S1 into fatigue calculation software, and calculating the fatigue life and the fatigue damage of the gearbox by combining the S-N curve of the material and the cycle number of each time sequence load.
The fatigue analysis method of the planetary transmission gearbox provided by the invention is described in detail above. The principles and embodiments of the present invention are explained herein using specific examples, which are presented only to assist in understanding the method and its core concepts. It should be noted that, for those skilled in the art, without departing from the principle of the present invention, it is possible to make various improvements and modifications to the present invention, and those improvements and modifications also fall within the scope of the claims of the present invention.
Claims (6)
1. A fatigue analysis method for a planetary transmission gearbox is characterized by comprising the following steps:
step S1: determining the rotation range of the meshing position according to the number of planet wheels in the gearbox, determining a plurality of different target meshing positions in the rotation range, and calculating the stress result of the gearbox corresponding to the target meshing positions;
step S2: establishing a function for interpolation for the position angle of each target meshing position, so that the function can cover two angle positions adjacent to the current angle position, and a position proportionality coefficient-angle curve is obtained;
and step S3: calculating an angle-time sequence of each target meshing position according to the rotating speed-time sequence of the gearbox;
and step S4: calculating a position load proportionality coefficient-time series from the position proportionality coefficient-angle curve, the angle-time series and the torque-time series of the gearbox;
step S5: calculating a position load proportional coefficient-time sequence under each working condition, and calculating a fatigue result of the gearbox through fatigue software; repeating the step S3 and the step S4 for all time sequence loads, inputting the obtained position load proportion coefficient-time sequence and the 5 groups of finite element stress results calculated in the step S1 into fatigue calculation software, and calculating by combining an S-N curve of a material and the cycle number of each time sequence load to obtain the fatigue life and the fatigue damage of the gearbox;
the step S1 includes:
establishing finite element models of a gearbox body and a gear ring, wherein load boundary conditions are divided into 5 load steps, the first 4 load steps respectively calculate the position of the gearbox body which rotates by 30 degrees in a 120-degree period at each meshing position under nominal input torque, apply the meshing force of a planet gear and an inner gear ring to the gear ring, and calculate to obtain 4 groups of stress results; the 5 th loading step is used for calculating a stress result of the box body under the action of gravity; obtaining 5 groups of finite element stress results;
the step S2 includes:
establishing a position proportionality coefficient-angle curve relating the first 4 groups of load steps to the meshing positions, which is specifically as follows:
position proportionality coefficient-angle curve equation under 0 degree position
Position proportionality coefficient-angle curve equation under 30 deg. position
Position proportionality coefficient-angle curve equation under 60 deg. position
Position proportionality coefficient-angle curve equation under 90 deg. position
2. A method of analyzing fatigue of an epicyclic gearbox according to claim 1, wherein said step S2 further comprises: and determining that the proportionality coefficient of the current angle position is 1 and the proportionality coefficients of the front and the back adjacent angle positions are 0.
3. A method for fatigue analysis of an epicyclic gearbox according to claim 1, wherein said step S1 comprises:
modeling is carried out on the planetary transmission gearbox by utilizing transmission system analysis software, and a solid model extraction node and a rigidity matrix of the planetary transmission gearbox are introduced into the transmission system analysis software by combining finite element software, wherein the node is used for connecting components on a planet carrier of the gearbox.
4. A method for fatigue analysis of a planetary drive gearbox according to claim 3, wherein said step S1 further comprises:
and calculating the model of the planetary transmission gearbox in the transmission system software, and calculating the acting force result of the gearbox at each target meshing position.
5. A method for fatigue analysis of a planetary drive gearbox according to claim 1, characterised in that said step S3 comprises:
according to the rotating speed-time sequence of the gearbox, setting an initial angle to be 0 degrees, wherein the angle of each time point is equal to the time interval between the current time point and the previous time point, multiplying the rotating speed of the previous time point by the angle of the previous time point, and then adding the angle of the previous time point; and analogizing to obtain the angle of each time point, and then taking the remainder of the angle of each time point to 120 degrees so that the value of each angle does not exceed 120 degrees, thereby obtaining the angle-time sequence.
6. A method for fatigue analysis of a planetary drive gearbox according to claim 5, characterised in that said step S4 comprises:
step S4-1: respectively substituting the angle-time sequences obtained in the step S3 into 4 sets of equations established in the step S2, and calculating to obtain 4 sets of position proportionality coefficients-time sequences;
step S4-2: according to the torque-time sequence of the gearbox, dividing the torque of each time point by the nominal torque used when the stress result is calculated in the step S1 to obtain a load proportionality coefficient-time sequence;
step S4-3: multiplying the 4 sets of position proportionality coefficient-time sequences obtained in the step S4-1 by the load proportionality coefficient-time sequences obtained in the step S4-2 respectively to obtain 4 sets of position load proportionality coefficient-time sequences related to the load size and the meshing position; because the size and the direction of the gravity are always unchanged, a group of gravity-time sequences with a proportionality coefficient of 1 are obtained; 5 sets of position load proportionality coefficient-time series were obtained.
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