CN112364551A - Fatigue analysis method for planetary transmission gearbox - Google Patents
Fatigue analysis method for planetary transmission gearbox Download PDFInfo
- Publication number
- CN112364551A CN112364551A CN202011453236.2A CN202011453236A CN112364551A CN 112364551 A CN112364551 A CN 112364551A CN 202011453236 A CN202011453236 A CN 202011453236A CN 112364551 A CN112364551 A CN 112364551A
- Authority
- CN
- China
- Prior art keywords
- gearbox
- angle
- load
- calculating
- time sequence
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Granted
Links
Images
Classifications
-
- G—PHYSICS
- G06—COMPUTING; CALCULATING OR COUNTING
- G06F—ELECTRIC DIGITAL DATA PROCESSING
- G06F30/00—Computer-aided design [CAD]
- G06F30/20—Design optimisation, verification or simulation
- G06F30/23—Design optimisation, verification or simulation using finite element methods [FEM] or finite difference methods [FDM]
-
- G—PHYSICS
- G06—COMPUTING; CALCULATING OR COUNTING
- G06F—ELECTRIC DIGITAL DATA PROCESSING
- G06F2119/00—Details relating to the type or aim of the analysis or the optimisation
- G06F2119/02—Reliability analysis or reliability optimisation; Failure analysis, e.g. worst case scenario performance, failure mode and effects analysis [FMEA]
-
- G—PHYSICS
- G06—COMPUTING; CALCULATING OR COUNTING
- G06F—ELECTRIC DIGITAL DATA PROCESSING
- G06F2119/00—Details relating to the type or aim of the analysis or the optimisation
- G06F2119/04—Ageing analysis or optimisation against ageing
-
- G—PHYSICS
- G06—COMPUTING; CALCULATING OR COUNTING
- G06F—ELECTRIC DIGITAL DATA PROCESSING
- G06F2119/00—Details relating to the type or aim of the analysis or the optimisation
- G06F2119/12—Timing analysis or timing optimisation
-
- G—PHYSICS
- G06—COMPUTING; CALCULATING OR COUNTING
- G06F—ELECTRIC DIGITAL DATA PROCESSING
- G06F2119/00—Details relating to the type or aim of the analysis or the optimisation
- G06F2119/14—Force analysis or force optimisation, e.g. static or dynamic forces
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
- Y02E10/00—Energy generation through renewable energy sources
- Y02E10/70—Wind energy
- Y02E10/72—Wind turbines with rotation axis in wind direction
Landscapes
- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Theoretical Computer Science (AREA)
- Computer Hardware Design (AREA)
- Evolutionary Computation (AREA)
- Geometry (AREA)
- General Engineering & Computer Science (AREA)
- General Physics & Mathematics (AREA)
- Testing Of Devices, Machine Parts, Or Other Structures Thereof (AREA)
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, the 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 torque transmission requirement, 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 which needs 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 a position proportionality coefficient-angle curve is obtained;
step S3: calculating an angle-time sequence of each target meshing position according to the rotating speed-time sequence of the gearbox;
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 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.
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 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.
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; 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.
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, 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.
Preferably, the step S4 includes:
step S4-1: respectively substituting the angle-time series 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 series;
step S4-2: dividing the torque of each time point by the nominal torque used when the stress result is calculated in the step S1 according to the torque-time sequence of the gearbox to obtain a load proportionality coefficient-time sequence;
step S4-3: multiplying the 4 sets of position proportionality coefficient-time series obtained in the step S4-1 by the load proportionality coefficient-time series obtained in the step S4-2, respectively, to obtain 4 sets of position load proportionality coefficient-time series related to the load size and the engagement 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.
Preferably, the step S5 includes:
repeating the step S3 and the step S4 for all time sequence loads, inputting the obtained position load proportionality coefficient-time sequence and the 5 sets 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 a position proportionality coefficient-angle curve is obtained; step S3: calculating an angle-time sequence of each target meshing position according to the rotating speed-time sequence of the gearbox; 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.
Drawings
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 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;
step S3: calculating an angle-time sequence of each target meshing position according to the rotating speed-time sequence of the gearbox;
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.
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:
the method comprises the steps of utilizing transmission system analysis software to model a planetary transmission gearbox, combining finite element software to guide entity model extraction nodes and rigidity matrixes of the planetary transmission gearbox into the transmission system analysis software, wherein the nodes are used for being connected with 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 gear box planet carrier 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 static strength analysis are limit load and gravity, and 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 degrees, 30 degrees, 60 degrees and 90 degrees, so that stress or strain of 4 positions is obtained, the relationship 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 and used as a static strength analysis result, based on the result, topology optimization is carried out on the planet carrier structure, so that the structure meets the rigidity requirement and the lightweight design requirement, and in order to obtain an accurate and convergent result, sub-model 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 coefficients-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 at 90 deg. positionScaling coefficient-angle curve equation
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 series 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 series;
step S4-2: dividing the torque of each time point by the nominal torque used when the stress result is calculated in the step S1 according to the torque-time sequence of the gearbox to obtain a load proportionality coefficient-time sequence;
step S4-3: multiplying the 4 sets of position proportionality coefficient-time series obtained in the step S4-1 by the load proportionality coefficient-time series obtained in the step S4-2, respectively, to obtain 4 sets of position load proportionality coefficient-time series related to the load size and the engagement 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.
Further, the step S5 includes:
repeating the step S3 and the step S4 for all time sequence loads, inputting the obtained position load proportionality coefficient-time sequence and the 5 sets 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, it is possible to make various improvements and modifications to the present invention without departing from the principle of the present invention, and those improvements and modifications also fall within the scope of the claims of the present invention.
Claims (10)
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;
step S3: calculating an angle-time sequence of each target meshing position according to the rotating speed-time sequence of the gearbox;
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.
2. The method for analyzing fatigue of an epicyclic transmission gearbox according to claim 1, wherein said step S4 comprises:
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.
3. The method for analyzing fatigue of an epicyclic transmission 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.
4. The method for analyzing fatigue of an epicyclic transmission 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.
5. The method for analyzing fatigue of an epicyclic transmission gearbox according to claim 4, 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.
6. A planetary transmission gearbox fatigue analysis method according to any of claims 1 to 5, characterized by said step S1 comprising:
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.
7. The method for analyzing fatigue of an epicyclic gearbox according to claim 6, wherein said step S2 comprises:
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
8. The method for analyzing fatigue of an epicyclic gearbox according to claim 6, wherein said step S3 comprises:
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.
9. The method for analyzing fatigue of an epicyclic gearbox according to claim 6, wherein said step S4 comprises:
step S4-1: respectively substituting the angle-time series 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 series;
step S4-2: dividing the torque of each time point by the nominal torque used when the stress result is calculated in the step S1 according to the torque-time sequence of the gearbox to obtain a load proportionality coefficient-time sequence;
step S4-3: multiplying the 4 sets of position proportionality coefficient-time series obtained in the step S4-1 by the load proportionality coefficient-time series obtained in the step S4-2, respectively, to obtain 4 sets of position load proportionality coefficient-time series related to the load size and the engagement 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.
10. The method for analyzing fatigue of an epicyclic gearbox according to claim 6, wherein said step S5 comprises:
repeating the step S3 and the step S4 for all time sequence loads, inputting the obtained position load proportionality coefficient-time sequence and the 5 sets 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.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202011453236.2A CN112364551B (en) | 2020-12-11 | 2020-12-11 | Fatigue analysis method for planetary transmission gearbox |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202011453236.2A CN112364551B (en) | 2020-12-11 | 2020-12-11 | Fatigue analysis method for planetary transmission gearbox |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN112364551A true CN112364551A (en) | 2021-02-12 |
| CN112364551B CN112364551B (en) | 2022-11-22 |
Family
ID=74536794
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202011453236.2A Active CN112364551B (en) | 2020-12-11 | 2020-12-11 | Fatigue analysis method for planetary transmission gearbox |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN112364551B (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN113177342A (en) * | 2021-05-25 | 2021-07-27 | 中国第一汽车股份有限公司 | Method for determining limit rotating speed of shaft retainer ring |
| CN114330073A (en) * | 2021-12-31 | 2022-04-12 | 重庆大学 | Planetary gear train power distribution characteristic calculation method |
Citations (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2011095519A2 (en) * | 2010-02-05 | 2011-08-11 | Vestas Wind Systems A/S | Method of operating a wind power plant |
| CN106126843A (en) * | 2016-06-28 | 2016-11-16 | 广东明阳风电产业集团有限公司 | A kind of Bladed blower fan load processing system based on Matlab |
| WO2017085694A2 (en) * | 2015-11-18 | 2017-05-26 | Romax Technology Limited | Driveline modeller |
| CN108446483A (en) * | 2018-03-16 | 2018-08-24 | 太原理工大学 | The Reliability assessment of wind farm method of meter and wind turbine generator drive system fatigue |
| CN110631848A (en) * | 2019-10-30 | 2019-12-31 | 长春工业大学 | Wheel and axle bending fatigue test device |
| CN111046512A (en) * | 2020-01-02 | 2020-04-21 | 重庆齿轮箱有限责任公司 | Planetary gearbox bolt analysis method |
| CN111189632A (en) * | 2020-01-10 | 2020-05-22 | 重庆交通大学 | Comprehensive test bed for fatigue life of gear |
| CN111515954A (en) * | 2020-05-06 | 2020-08-11 | 大连理工大学 | Method for generating high-quality motion path of mechanical arm |
-
2020
- 2020-12-11 CN CN202011453236.2A patent/CN112364551B/en active Active
Patent Citations (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2011095519A2 (en) * | 2010-02-05 | 2011-08-11 | Vestas Wind Systems A/S | Method of operating a wind power plant |
| WO2017085694A2 (en) * | 2015-11-18 | 2017-05-26 | Romax Technology Limited | Driveline modeller |
| CN106126843A (en) * | 2016-06-28 | 2016-11-16 | 广东明阳风电产业集团有限公司 | A kind of Bladed blower fan load processing system based on Matlab |
| CN108446483A (en) * | 2018-03-16 | 2018-08-24 | 太原理工大学 | The Reliability assessment of wind farm method of meter and wind turbine generator drive system fatigue |
| CN110631848A (en) * | 2019-10-30 | 2019-12-31 | 长春工业大学 | Wheel and axle bending fatigue test device |
| CN111046512A (en) * | 2020-01-02 | 2020-04-21 | 重庆齿轮箱有限责任公司 | Planetary gearbox bolt analysis method |
| CN111189632A (en) * | 2020-01-10 | 2020-05-22 | 重庆交通大学 | Comprehensive test bed for fatigue life of gear |
| CN111515954A (en) * | 2020-05-06 | 2020-08-11 | 大连理工大学 | Method for generating high-quality motion path of mechanical arm |
Non-Patent Citations (2)
| Title |
|---|
| 刘嘉慧等: "多工况下风电齿轮箱联接螺栓疲劳寿命分析", 《机械研究与应用》 * |
| 马洪义; 谢里阳; 谭秀峰: "风力发电机齿轮箱齿根弯曲疲劳寿命仿真技术与方法研究", 《太阳能学报》 * |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN113177342A (en) * | 2021-05-25 | 2021-07-27 | 中国第一汽车股份有限公司 | Method for determining limit rotating speed of shaft retainer ring |
| CN113177342B (en) * | 2021-05-25 | 2022-04-01 | 中国第一汽车股份有限公司 | Method for determining limit rotating speed of shaft retainer ring |
| CN114330073A (en) * | 2021-12-31 | 2022-04-12 | 重庆大学 | Planetary gear train power distribution characteristic calculation method |
Also Published As
| Publication number | Publication date |
|---|---|
| CN112364551B (en) | 2022-11-22 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN105677980B (en) | The modal synthesis Dynamic Modeling and analysis method of Automobile drive bridge system | |
| CN112364551B (en) | Fatigue analysis method for planetary transmission gearbox | |
| Shweiki et al. | Transmission Error and strain analysis of lightweight gears by using a hybrid FE-analytical gear contact model | |
| CN109871652A (en) | A kind of gear pair Abrasion prediction method based on dynamic engagement power | |
| Nelson et al. | Simplified kinematic analysis of bevel epicyclic gear trains with application to power-flow and efficiency analyses | |
| CN106960093A (en) | A kind of transmission system method for numerical simulation for considering gear and bearing Non-linear coupling | |
| CN111428409B (en) | Equation solving method for mechanical nonlinear vibration analysis | |
| Zhang et al. | Coupled dynamic characteristics of wind turbine gearbox driven by ring gear considering gravity | |
| Zhang et al. | Investigation on planetary gearbox fault mechanism under variable speed conditions based on rigid-flexible coupling dynamics model | |
| Huang et al. | Dynamic characteristics analysis and experimental research on a new type planetary gear apparatus with small tooth number difference | |
| Lauibi Esmail | Meshing efficiency analysis of two degree-of-freedom epicyclic gear trains | |
| Sun et al. | Design and transmission error analysis of CBR reducer | |
| CN106326530A (en) | Time-varying structure modal parameter identification method based on right matrix fraction model | |
| CN111027156A (en) | Method for analyzing reliability of transmission precision of industrial robot speed reducer with crack gear | |
| CN110807278A (en) | Three-dimensional solid unit modeling method of gear system | |
| Zhang et al. | Similarity and experimental prediction on load sharing performance of planetary gear transmission system | |
| CN111046512B (en) | Analysis method for planetary gear box bolt | |
| CN102278423B (en) | Analytical method and system of mechanical efficiency of planet gear mechanism | |
| Algin et al. | Kinematic and dynamic computation of vehicle transmission based on regular constructs | |
| Yang et al. | Experimental and simulation analysis on windage power loss of herringbone gear pair | |
| Yaoguo et al. | A new analysis technology of the vibration characteristic of the gearbox case of herringbone gear reducer | |
| CN104361220B (en) | A kind of gear train stress field computational methods for considering thermosetting coupling | |
| CN113465961A (en) | Full-size ground loading test system for transmission chain of wind turbine generator and control method thereof | |
| Zhang et al. | Similarity and vibration signal prediction of planetary gear transmission system based on hierarchy analysis | |
| Lu et al. | Research on vibration characteristics of multistage gears transmission system driven by internal and external excitation |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| PB01 | Publication | ||
| PB01 | Publication | ||
| SE01 | Entry into force of request for substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| GR01 | Patent grant | ||
| GR01 | Patent grant |