CN107992688A - Locomotive traction gear Automated Design equipment and automatic design method - Google Patents
Locomotive traction gear Automated Design equipment and automatic design method Download PDFInfo
- Publication number
- CN107992688A CN107992688A CN201711282101.2A CN201711282101A CN107992688A CN 107992688 A CN107992688 A CN 107992688A CN 201711282101 A CN201711282101 A CN 201711282101A CN 107992688 A CN107992688 A CN 107992688A
- Authority
- CN
- China
- Prior art keywords
- gear
- locomotive traction
- tooth
- traction gear
- locomotive
- 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
Classifications
-
- G—PHYSICS
- G06—COMPUTING; CALCULATING OR COUNTING
- G06F—ELECTRIC DIGITAL DATA PROCESSING
- G06F30/00—Computer-aided design [CAD]
- G06F30/10—Geometric CAD
- G06F30/15—Vehicle, aircraft or watercraft design
Landscapes
- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Geometry (AREA)
- General Physics & Mathematics (AREA)
- Theoretical Computer Science (AREA)
- Aviation & Aerospace Engineering (AREA)
- Computational Mathematics (AREA)
- Mathematical Analysis (AREA)
- Mathematical Optimization (AREA)
- Pure & Applied Mathematics (AREA)
- Computer Hardware Design (AREA)
- Evolutionary Computation (AREA)
- General Engineering & Computer Science (AREA)
- Automation & Control Theory (AREA)
- Gears, Cams (AREA)
Abstract
The invention discloses a kind of locomotive traction gear Automated Design equipment and automatic design method, Automated Design equipment is divided into three modules：Locomotive traction gear scheme Automated Design module；Locomotive traction gear physical dimension computing module；Locomotive traction gear accuracy computation module.Automatic design method, A, locomotive traction gear Automated Design module, designs multigroup designing scheme；B, locomotive traction gear physical dimension computing module selects one group of rational designing scheme from the designing scheme of locomotive traction gear Automated Design module, calculate the gear geometry parameter of the designing scheme, when the gear geometry parameter being calculated is undesirable, alarm；C, locomotive traction gear accuracy computation module calculates the accuracy value of traction gear after the calculating of locomotive traction gear physical dimension is errorless.This device and method has the function of automatic scheme formulation.There is alarm etc..The error of traditional calculations is can effectively avoid, greatly improves design efficiency.
Description
Technical Field
The invention relates to automatic design equipment and an automatic design method for a locomotive traction gear.
Background
The locomotive traction gear is an important component of the locomotive, and the locomotive is developing towards high speed and heavy load along with the progress of production and scientific technology. The gear parameters of the locomotive are complicated, the design calculation is influenced by a plurality of factors and parameters, great errors can be caused by carelessness, great energy and endurance are required, and great obstacles are created for rapid scheme making.
At present, gear calculation software on the market is more, the software is obtained by listing relevant formulas according to gear design standards, the purchase cost is high, the usability of the locomotive is poor, the operation is complex, a plurality of functions cannot be used, and the design cost performance of a locomotive traction gear is low.
The existing gear design software and method on the market have the following defects: the purchasing cost is high, a plurality of functions can not be used, the locomotive usability is poor, the operation is complicated, and design experience values and parameter range prompts of related parameters are avoided.
Disclosure of Invention
The invention solves the technical problem that the existing automatic design equipment and design method for the locomotive traction gear have the defects, provides the automatic design equipment and the automatic design method for the locomotive traction gear, sets the range value of related parameters according to the design experience of the locomotive traction gear, has the functions of warning prompt and the like, can automatically set multiple groups of gear design schemes by software, can calculate the geometric dimension and the precision of the gear after selecting a group of reasonable schemes, and provides a convenient and quick method for the design of the locomotive traction gear.
The technical scheme adopted by the invention is as follows: the automatic design equipment for the locomotive traction gear comprises an automatic design module for the locomotive traction gear, a geometric dimension calculation module for the locomotive traction gear and a precision calculation module for the locomotive traction gear, wherein the automatic design module for the locomotive traction gear determines a plurality of groups of gear design schemes according to known input and constraint conditions, then the geometric dimension calculation module for the locomotive traction gear selects one group of design schemes, sets a deflection coefficient, calculates geometric parameters of the gear, and carries out precision calculation when the dimension calculation of the geometric dimension calculation module for the locomotive traction gear is correct, and finally outputs a result.
An automatic design method for a locomotive traction gear,
A. inputting the known conditions into a locomotive traction gear automatic design module through an input system, establishing gear design constraint conditions by the locomotive traction gear automatic design module, and designing a plurality of groups of design schemes after the constraint conditions are checked to be qualified;
B. the locomotive traction gear geometric dimension calculation module selects a group of reasonable design schemes from the design schemes of the locomotive traction gear automatic design module, sets a deflection coefficient according to the principle that a driving gear and a driven gear keep positive deflection, further calculates the gear geometric parameters of the design schemes, and prompts appear on the interface when the calculated gear geometric parameters are smaller than or exceed the set empirical value, and causes of errors appear after clicking;
C. and the locomotive traction gear precision calculation module calculates the precision value of the traction gear after the geometric dimension of the locomotive traction gear is calculated to be correct.
The step A specifically comprises the following steps:
(1) inputting known parameters such as wheel abrasion diameter, locomotive limit, gearbox wall thickness, given center distance A, pressure angle alpha, transmission ratio range and the like into a locomotive traction gear automatic design module through an input system;
(2) a locomotive traction gear automatic design module establishes gear design constraint conditions;
(3) automatic module m for automatic design module of locomotive traction gear n Range, determining tooth number Z;
(4) the automatic design module of the locomotive traction gear determines the tooth number Z of the driving gear according to the transmission ratio and the standard center distance 1 And number of driven gear teeth Z 2 ；
(5) And after the constraint conditions are calculated and inspected to be qualified, the automatic design module of the locomotive traction gear outputs a plurality of groups of tooth numbers and modules.
The modulus ranges from 7 to 12, and the pressure angle alpha is 20 degrees, 22.5 degrees and 25 degrees.
The number of teeth Z, the given center distance A and the modulus m n Should satisfy Z < 2A/m n 。
The standard center distance A' and the modulus m n Pressure angle alpha, number of teeth of driving gear Z 1 And number of driven gear teeth Z 2 The functional relationship between the two is
The constraint condition comprises the maximum value D of the radius of the addendum circle max Overlap ratio ε α Tooth top thickness, slip ratio and tooth profile interference parameters.
The maximum value of the addendum circle radius meets D max R-mh-jx-hd-xj is less than or equal to R, wherein: r-wheel radius, mh-wheel abrasion loss, jx-locomotive limit, hd-gearbox wall thickness, xj-tooth top and box body clearance;
the contact ratio epsilon α Satisfies epsilon α ≥1.4；
The tooth crest thickness is more than 0.4 times of modulus and more than 3mm, namely:in the formula: d a Diameter of addendum circle, m n -the modulus; s a Thickness of addendum circle, alpha-pressure angle, Z-number of teeth, m n -a modulus; the slip ratio should satisfy the difference of the slip ratio of the driving gear and the driven gear is 0.1, namely:
in the formula eta 1 Slip ratio of the driving gear, η 2 From gear ratio, Z 1 Number of driving gear teeth, Z 2 Number of driven gear teeth, α α1 -a drive gear addendum circle pressure angle,α α2 slave gear tooth tip circle pressure angle, mu-gear ratio, alpha t "dog angle;
the tooth profile interference parameters comprise curvature radius rho at a tooth profile dividing point l And radius of curvature at root of working tooth ρ p And the curvature radius rho at the tooth profile dividing point l Less than radius of curvature rho at root of working tooth p Namely:
ρ l ＝0.5×d×sinα t -[han * +cn * -r * (1-sinα n )-X]·m n /sinα t ≤ρ P
ρ p ＝a'·sinα t '-0.5d b ·tanα a
in the formula: d-reference circle diameter, alpha t Pressure angle, h an * -coefficient of addendum height, c n * -coefficient of tip clearance, r-coefficient of root fillet radius, α n Pressure angle, X-deflection coefficient, d b Diameter of base circle, m n Modulus, a' -centre distance, α t Angle of mesh, a a Addendum circle pressure angle.
The geometric parameters of the gear comprise the radius of an addendum circle and a module m n Number of teeth Z, addendum circle diameter, tooth height, addendum circle pressure angle, tooth span number, common normal length, contact ratio epsilon α Tooth top thickness, slip ratio, tooth profile interference parameters; the errors and the error reasons comprise: maximum radius of addendum circle D max &Wheel radius, abrasion loss, locomotive clearance, gear box wall thickness, tooth top and box body clearance, and at the moment, an error warning appears on the interface to prompt to reselect a scheme; the thickness of the tooth edge is 1.56 times smaller than the height of the tooth, and the interface prompts that the safety margin of the tooth edge is smaller and the strength check is needed; the contact ratio is less than 1.4, and the interface prompts to revise the tooth number again to make the contact ratio greater than 1.4; the thickness of the tooth top is less than 0.4 times of the modulus or less than 3mm, and at the moment, the interface prompts readjustment of the tooth number and the displacement coefficient; when the difference of the slip ratio is larger than 0.1, the interface prompting difference is larger, and the displacement coefficient is considered to be adjusted; the curvature radius at the tooth profile boundary point is larger than that at the working tooth root, and the interface prompts tooth profile interference at the moment; the modification coefficient of the driving gear is smaller than that of the driven gearThe interface prompts the reassignment of the shift coefficients.
The precision values comprise the diameter of a working circle, the diameter difference between the working circle and a forming circle, the diameter of the forming circle, the pressure angle at the forming circle, the spread angle at the addendum circle, the spread angle at a pitch circle, the tooth thickness deviation, the tooth thickness tolerance, the maximum assembly backlash, the normal deviation and the nominal tooth thickness.
The invention has the following beneficial effects: the design device and the design method special for the locomotive traction gear have an automatic scheme making function. The design method summarizes the design experience of the locomotive traction gear, sets the experience value of the relevant parameter, and has the functions of warning and prompting when the calculated parameter exceeds the experience value. The design method replaces manual calculation, is convenient and visual to operate, can effectively avoid errors of traditional calculation, and greatly improves the design efficiency.
Drawings
FIG. 1 is a diagram of an automatic design equipment for a locomotive traction gear.
FIG. 2 is a flow chart of an automated design module calculation for a method of automatically designing a locomotive traction gear.
Detailed Description
The following will further describe the automatic design equipment and the automatic design method of the locomotive traction gear with reference to the attached drawings.
The automatic design equipment for the locomotive traction gear is divided into three modules: a locomotive traction gear scheme automatic design module; a locomotive traction gear geometric dimension calculation module; locomotive traction gear precision calculation module. The automatic design module of the locomotive traction gear scheme comprises: the module uses the thought of mechanical optimization design to take the tooth number and the modulus as optimization target parameters, and takes the design experience values of addendum circle radius, pressure angle, tooth edge thickness, contact ratio, tooth top thickness, sliding ratio and tooth shape interference inspection as constraint conditions, so as to realize the automatic scheme design function of the locomotive traction gear, and the module can determine a plurality of groups of design schemes.
The geometric dimension calculation module of the locomotive traction gear comprises: and selecting a group of reasonable design schemes from the schemes determined by the automatic design module, setting a displacement coefficient to further calculate the addendum circle radius, the modulus, the contact ratio, the tooth top thickness, the sliding ratio, the tooth profile interference test value and the like, wherein when the calculated value is smaller than or exceeds the set empirical value, a red prompt appears on the interface, and the error reason appears after clicking.
The locomotive traction gear precision calculation module: and the geometric dimension in the dimension calculation module enters the precision calculation module after being calculated without errors, and tooth profile tolerance, tooth thickness deviation, tooth thickness tolerance, maximum assembly backlash, normal line deviation, nominal tooth thickness and the like are calculated.
The automatic design module of the locomotive traction gear determines a plurality of groups of gear design schemes according to known input and constraint conditions, then the geometric dimension calculation module of the locomotive traction gear selects a group of design schemes, sets a deflection coefficient and calculates geometric parameters of the gear, the precision calculation module of the locomotive traction gear performs precision calculation when the dimension calculation of the geometric dimension calculation module of the locomotive traction gear is correct, and finally a result is output.
An automatic design method for a locomotive traction gear,
A. inputting known conditions into an automatic design module of a locomotive traction gear through a locomotive, establishing gear design constraint conditions by the automatic design module of the locomotive traction gear, and designing a plurality of groups of design schemes after the constraint conditions are checked to be qualified;
the automatic design process is as follows, as shown in FIG. 2:
(1) the method comprises the following steps that known parameters such as wheel abrasion diameter, locomotive limit, gearbox wall thickness, given center distance A, pressure angle alpha, transmission ratio range and the like are input into a locomotive traction gear automatic design module through a locomotive;
(2) the automatic design module of the locomotive traction gear establishes a gear design constraint condition;
(3) automatic module m for automatic design module of locomotive traction gear n The range, the determined tooth number Z, the modulus range is 7-12, and the pressure angle alpha is 20 degrees, 22.5 degrees and 25 degrees; to ensure positive deflection of the gear, the number of teeth Z, the given center distance A andmodulus m n Should satisfy Z < 2A/m n And is an integer;
(4) determining the tooth number Z1 of the driving gear and the tooth number Z2 of the driven gear according to parameters such as transmission ratio and the like; the function relationship among the standard center distance A', the modulus mn, the pressure angle alpha, the number of teeth Z1 of the driving gear and the number of teeth Z2 of the driven gear is
(5) And after the constraint conditions are calculated and inspected to be qualified, the automatic design module of the locomotive traction gear outputs a plurality of groups of tooth numbers and modules.
B. The locomotive traction gear geometric dimension calculation module selects a group of reasonable design schemes from the design schemes of the locomotive traction gear automatic design module, sets a deflection coefficient according to the principle that a driving gear and a driven gear keep positive deflection, further calculates the gear geometric parameters of the design schemes, and when the calculated gear geometric parameters are smaller than or exceed the set empirical value, a red prompt appears on the interface, and an error reason appears after clicking; errors and error causes include: maximum value of addendum circle radius D max &Wheel radius, abrasion loss, locomotive clearance, gear box wall thickness, tooth top and box body clearance, and at the moment, an error warning appears on the interface to prompt to reselect a scheme; the thickness of the tooth edge is 1.56 times smaller than the height of the tooth, and the interface prompts that the safety margin of the tooth edge is smaller and the strength check is needed; the contact ratio is less than 1.4, and the interface prompts to revise the tooth number again to make the contact ratio greater than 1.4; the thickness of the tooth top is less than 0.4 time of the modulus or less than 3mm, and the interface prompts readjustment of the tooth number and the displacement coefficient at the moment; when the difference of the slip ratio is larger than 0.1, the interface prompt difference is larger, and the adjustment of the deflection coefficient is considered; the curvature radius at the tooth profile dividing point is larger than that at the working tooth root, and the interface prompts tooth profile interference at the moment; the driving gear shift coefficient is smaller than the driven gear shift coefficient, and the interface prompts the redistribution of the shift coefficient.
C. And the locomotive traction gear precision calculation module calculates the precision value of the traction gear after the geometric dimension of the locomotive traction gear is calculated to be correct. The precision value comprises the diameter of a working circle, the diameter difference between the working circle and a forming circle, the diameter of the forming circle, the pressure angle at the forming circle, the spread angle at the addendum circle, the spread angle at a pitch circle, the tooth thickness deviation, the tooth thickness tolerance, the maximum assembly backlash, the normal deviation and the nominal tooth thickness.
The constraints are as follows:
1) The maximum radius of addendum circle satisfies D max R-mh-jx-hd-xj is less than or equal to R, wherein: r-wheel radius, mh-wheel abrasion loss, jx-locomotive limit, hd-gear box wall thickness, xj-tooth top and box body gap;
the contact ratio epsilon α Satisfies epsilon α ≥1.4；
2) The tooth top thickness is more than 0.4 times modulus and more than 3mm, namely:in the formula: d a Diameter of addendum circle, m n -the modulus; s a Thickness of addendum circle, alpha-pressure angle, Z-number of teeth, m n -a modulus;
3) The slip ratio should satisfy the difference of the slip ratio of the driving gear and the driven gear is 0.1, namely:
in the formula eta 1 Slip ratio of the driving gear, η 2 From gear ratio, Z 1 Number of driving gear teeth, Z 2 Number of driven gear teeth, α α1 Pressure angle of addendum circle of the driving gear, α α2 Slave gear tooth tip circle pressure angle, mu-gear ratio, alpha t "dog angle;
4) The tooth profile interference parameters comprise curvature radius rho at a tooth profile dividing point l And radius of curvature at root of working tooth ρ p And the curvature radius rho at the tooth profile dividing point l Less than radius of curvature rho at root of working tooth p Namely:
ρ l ＝0.5×d×sinα t -[han * +cn * -r * (1-sinα n )-X]·m n /sinα t ≤ρ P
ρ p ＝a'·sinα t '-0.5d b ·tanα a
in the formula: d-reference circle diameter, alpha t Angle of pressure, h an * -coefficient of addendum height, c n * -coefficient of tip clearance, r-coefficient of root fillet radius, α n Pressure angle, X-deflection coefficient, d b Diameter of base circle, m n Modulus, a' -center distance, α t Angle of mesh, a a Addendum circle pressure angle.
Claims (10)
1. Locomotive traction gear automatic design equipment which characterized in that: the automatic design module of the locomotive traction gear determines a plurality of groups of gear design schemes according to known input and constraint conditions, then the geometric dimension calculation module of the locomotive traction gear selects a group of design schemes, sets a deflection coefficient and calculates geometric parameters of the gear, and the precision calculation module of the locomotive traction gear performs precision calculation when the dimension calculation of the geometric dimension calculation module of the locomotive traction gear is correct and finally outputs a result.
2. The automatic design method of a locomotive traction gear using the automatic design device of a locomotive traction gear according to claim 1, characterized in that:
A. inputting known conditions into an automatic design module of a locomotive traction gear through an input system of the locomotive, establishing gear design constraint conditions by the automatic design module of the locomotive traction gear, and designing a plurality of groups of design schemes after the constraint conditions are checked to be qualified;
B. the locomotive traction gear geometric dimension calculation module selects a group of reasonable design schemes from the design schemes of the locomotive traction gear automatic design module, sets a deflection coefficient according to the principle that a driving gear and a driven gear keep positive deflection, further calculates the gear geometric parameters of the design schemes, and prompts appear on the interface when the calculated gear geometric parameters are smaller than or exceed the set empirical value, and causes of errors appear after clicking;
C. and the locomotive traction gear precision calculation module calculates the precision value of the traction gear after the geometric dimension of the locomotive traction gear is calculated to be correct.
3. The method of automatically designing a locomotive traction gear according to claim 2, wherein: the step A is specifically as follows:
(1) known parameters such as wheel abrasion diameter, locomotive limit, gearbox wall thickness, given center distance A, pressure angle alpha, transmission ratio range and the like are input into a locomotive traction gear automatic design module through an input system;
(2) a locomotive traction gear automatic design module establishes gear design constraint conditions;
(3) automatic module m for automatic design module of locomotive traction gear n Range, determining tooth number Z;
(4) the locomotive traction gear automatic design module calculates and determines the tooth number Z of the driving gear according to the transmission ratio and the standard center distance 1 And number of driven gear teeth Z 2 ；
(5) And after the constraint condition calculation and inspection are qualified, the automatic design module of the locomotive traction gear outputs a plurality of groups of tooth numbers and modules.
4. The method of automatically designing a locomotive traction gear according to claim 3, wherein: the modulus ranges from 7 to 12, and the pressure angle alpha is 20 degrees, 22.5 degrees and 25 degrees.
5. The method of automatically designing a locomotive traction gear according to claim 3, wherein: the number of teeth Z, the given center distance A and the modulus m n Should satisfy Z < 2A/m n 。
6. The method of automatically designing a locomotive traction gear according to claim 3, wherein: the standard center distance A' and the modulus m n Pressure angle alpha, number of teeth of driving gear Z 1 And number of driven gear teeth Z 2 The functional relationship between the two is
7. The automatic design method for locomotive traction gears according to claim 2 or 3, characterized in that: the constraint condition comprises the maximum value D of the addendum circle radius max Coincidence degree epsilon α Tooth top thickness, slip ratio and tooth profile interference parameters.
8. The method of automatically designing a locomotive traction gear according to claim 7, wherein: the maximum value of the addendum circle radius satisfies D max R-mh-jx-hd-xj is less than or equal to R, wherein: r-wheel radius, mh-wheel abrasion loss, jx-locomotive limit, hd-gear box wall thickness, xj-tooth top and box body gap;
the contact ratio epsilon α Satisfies epsilon α ≥1.4；
The tooth crest thickness is more than 0.4 times of modulus and more than 3mm, namely:in the formula: d a Diameter of addendum circle, m n -the modulus; s. the a Thickness of addendum circle, alpha-pressure angle, Z-number of teeth, m n -a modulus; the slip ratio should satisfy the difference of the slip ratio of the driving gear and the driven gear is 0.1, namely:
in the formula eta 1 Slip ratio of the driving gear, η 2 From gear ratio, Z 1 Number of driving gear teeth, Z 2 Number of driven gear teeth, α α1 Pressure angle of addendum circle of the driving gear, α α2 Slave gear tooth tip circle pressure angle, mu-gear ratio, alpha t "dog angle;
the tooth profile interference parameters comprise curvature radius rho at a tooth profile dividing point l And radius of curvature at root of working tooth ρ p And at the division point of the tooth profileRadius of curvature ρ l Less than radius of curvature rho at root of working tooth p Namely:
ρ l ＝0.5×d×sinα t -[han * +cn * -r * (1-sinα n )-X]·m n /sinα t ≤ρ P
ρ p ＝a'·sinα t '-0.5d b ·tanα a
in the formula: d-reference circle diameter, alpha t Angle of pressure, h an * -coefficient of addendum height, c n * -coefficient of tip clearance, r-coefficient of root fillet radius, α n Pressure angle, X-deflection coefficient, d b Diameter of base circle, m n Modulus, a' -center distance, α t ' engaging corner, a a Addendum circle pressure angle.
9. The method of automatically designing a locomotive traction gear according to claim 2, wherein: the geometric parameters of the gear comprise addendum circle radius and module m n Tooth number Z, addendum circle diameter, tooth height, addendum circle pressure angle, tooth span number, common normal length, contact ratio epsilon α Tooth top thickness, slip ratio and tooth profile interference parameters; the errors and error reasons comprise: maximum value of addendum circle radius D max &Wheel radius, abrasion loss, locomotive clearance, gear box wall thickness, tooth top and box body clearance, and at the moment, an error warning appears on the interface to prompt to reselect a scheme; the thickness of the tooth rim is 1.56 times less than the height of the tooth, and the interface prompts that the safety margin of the tooth rim is small and the strength check is needed; the contact ratio is less than 1.4, and the interface prompts to re-correct the number of teeth to make the contact ratio greater than 1.4; the thickness of the tooth top is less than 0.4 time of the modulus or less than 3mm, and the interface prompts readjustment of the tooth number and the displacement coefficient at the moment; when the difference of the slip ratio is larger than 0.1, the interface prompting difference is larger, and the displacement coefficient is considered to be adjusted; the curvature radius at the tooth profile dividing point is larger than that at the working tooth root, and the interface prompts tooth profile interference at the moment; the driving gear deflection coefficient is smaller than the driven gear deflection coefficient, and the interface prompts the redistribution of the deflection coefficient.
10. The method of automatically designing a locomotive traction gear according to claim 2, wherein: the precision value comprises a working circle diameter, a difference between the working circle and a forming circle, a forming circle diameter, a forming circle pressure angle, a forming circle expansion angle, an addendum circle expansion angle, a pitch circle expansion angle, a tooth thickness deviation, a tooth thickness tolerance, a maximum assembly backlash, a normal deviation and a nominal tooth thickness.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201711282101.2A CN107992688B (en) | 2017-12-07 | 2017-12-07 | Automatic design equipment and automatic design method for locomotive traction gear |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201711282101.2A CN107992688B (en) | 2017-12-07 | 2017-12-07 | Automatic design equipment and automatic design method for locomotive traction gear |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN107992688A true CN107992688A (en) | 2018-05-04 |
| CN107992688B CN107992688B (en) | 2021-09-24 |
Family
ID=62036415
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201711282101.2A Active CN107992688B (en) | 2017-12-07 | 2017-12-07 | Automatic design equipment and automatic design method for locomotive traction gear |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN107992688B (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN110056639A (en) * | 2019-04-25 | 2019-07-26 | 浙江吉利控股集团有限公司 | Calculation method and system for gear train |
Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US20130035197A1 (en) * | 2011-07-29 | 2013-02-07 | Agustawestland S.P.A. | Planetary gear train and corresponding production method |
| CN104408239A (en) * | 2014-11-11 | 2015-03-11 | 山东科技大学 | Accurate constraint condition-based cylindrical gearing optimization design method and accurate constraint condition-based cylindrical gearing CAD (computer-aided design) optimization design system |
| CN106528991A (en) * | 2016-10-27 | 2017-03-22 | 湖北汽车工业学院 | Method for performing optimization design on gearbox based on Taylor random finite element |
| CN107194124A (en) * | 2017-06-23 | 2017-09-22 | 重庆长安汽车股份有限公司 | A kind of helical gear design method of speed changer |
-
2017
- 2017-12-07 CN CN201711282101.2A patent/CN107992688B/en active Active
Patent Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US20130035197A1 (en) * | 2011-07-29 | 2013-02-07 | Agustawestland S.P.A. | Planetary gear train and corresponding production method |
| CN104408239A (en) * | 2014-11-11 | 2015-03-11 | 山东科技大学 | Accurate constraint condition-based cylindrical gearing optimization design method and accurate constraint condition-based cylindrical gearing CAD (computer-aided design) optimization design system |
| CN106528991A (en) * | 2016-10-27 | 2017-03-22 | 湖北汽车工业学院 | Method for performing optimization design on gearbox based on Taylor random finite element |
| CN107194124A (en) * | 2017-06-23 | 2017-09-22 | 重庆长安汽车股份有限公司 | A kind of helical gear design method of speed changer |
Non-Patent Citations (2)
| Title |
|---|
| 孟祥战: "航空发动机星型齿轮传动系统优化设计", 《中国优秀硕士学位论文全文数据库 工程科技Ⅱ辑》 * |
| 郭培培 等: "齿轮自动设计与建模一体化系统实现", 《工具技术》 * |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN110056639A (en) * | 2019-04-25 | 2019-07-26 | 浙江吉利控股集团有限公司 | Calculation method and system for gear train |
Also Published As
| Publication number | Publication date |
|---|---|
| CN107992688B (en) | 2021-09-24 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN108533715B (en) | Bidirectional conjugate tooth profile design method for harmonic gear transmission | |
| GB2564919B (en) | Gearsets | |
| CN109707822B (en) | Design method of small-modulus harmonic transmission meshing tooth form applied to robot and detector | |
| KR101679632B1 (en) | Gearing of a gearwheel | |
| US9267594B2 (en) | Controlled relative radius of curvature forged bevel gears with involute section | |
| CN108730480B (en) | Cycloidal gear of RV reducer and tooth profile reverse active modification method thereof | |
| CN107908857B (en) | Tooth surface principle error modeling method during shaping and grinding of tooth-direction profile modification helical gear | |
| CN109376456B (en) | Numerical calculation method for tooth surface load contact performance of spiral bevel gear with installation error | |
| CN106392200A (en) | Composite shape correction method for tooth contour of cycloidal gear of RV reducer | |
| CN110375054B (en) | Asymmetric gear design method based on tooth profile inclination deviation | |
| CN111299982B (en) | Shape-modifying machining process for gear of agricultural machine | |
| CN104889501A (en) | Non-full-symmetry involute gear, gear cutting hob special for same, and machining method of non-full-symmetry involute gear | |
| CN110008610A (en) | Cycloid tooth profile subsection optimization design method | |
| CN107992688A (en) | Locomotive traction gear Automated Design equipment and automatic design method | |
| CN108775376A (en) | A kind of straight bevel gear is secondary and its axial modification method | |
| CN105127521B (en) | A kind of hobboing cutter and processing method for being used to process Double Involute Gear | |
| CN110039123B (en) | Method for processing inverted cone teeth by variable-pressure-angle hob | |
| CN104063605A (en) | Method for checking gear involute tooth profile error | |
| Kissling et al. | Face gears: Geometry and strength | |
| CN113487180B (en) | Gear tooth surface evaluation method based on cloud platform | |
| CN110887457B (en) | Method for calculating cross section area of wheel end with any tooth type | |
| CN105179600B (en) | Double big negative addendum modification Involutes Gears Transmission devices | |
| CN110052666B (en) | Double-spelling curve type gear hob | |
| WO2020207237A1 (en) | Gear-formation-oriented machining method for matching gear | |
| CN101339017A (en) | Gear base tangent length, normal pitch and deviation measurement method and system |
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 |