CN107153736A - The gear pair meshing characteristic analysis method to correction of the flank shape is roused in a kind of consideration of amendment - Google Patents
The gear pair meshing characteristic analysis method to correction of the flank shape is roused in a kind of consideration of amendment Download PDFInfo
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Abstract
The gear pair meshing characteristic analysis method to correction of the flank shape is roused the present invention relates to a kind of consideration of amendment, this method is to obtain the basic parameter of gear pair and rouse to profile modifying parameters, along facewidth Directional Decomposition it is N number of independent and uniform web gear by the gear teeth of gear pair, based on the tooth profile error roused to profile modifying gear pair, using the gear pair meshing characteristic analysis method for considering extension engagement influence, the time-variant mesh stiffness for obtaining every plate sheet gear pair is calculated；Engaging tooth wheel set threedimensional model containing from drum to correction of the flank shape is set up by three-dimensional drawing simulation softward, threedimensional model is imported into ANSYS softwares sets up three-dimensional finite element contact model, solves the time-variant mesh stiffness data in the whole engagement process of gear；The analysis method modeling process of the present invention is simple, and amount of calculation is small, requires relatively low to computer, result of calculation is accurately true.
Description
Technical field
The invention belongs to mechanical kinetics technical field, and in particular to consider gear pair of the drum to correction of the flank shape to a kind of amendment
Meshing characteristic analysis method.
Background technology
At present, it is existing to consider that drum mainly has following 2 kinds of methods to the gear pair meshing characteristic analysis method of correction of the flank shape：
1. based on commercial finite element analysis software
Three-dimensional CAD model is imported into commercial finite element analysis software or three-dimensional mould is directly set up in finite element software
Type, selects suitable unit and material parameter, and mesh generation is carried out to threedimensional model, sets up the finite element contact of engaging tooth wheel set
Model, setting suitably constrains and selects appropriate method for solving to analyze the meshing characteristic of gear pair.But utilize existing
Commercial finite element analysis software to consider drum be engaged specificity analysis to the gear pair of correction of the flank shape when, modeling process is complicated and numerous
Weight, computational efficiency is low, requires higher to computing power, and using nibbling that different modeling pattern and cell type are obtained
Close characteristic and also have larger gap.
2. the modeling method based on cantilever beam
Gear tooth is simplified to Flexural cantilever model, rigidity modeling is engaged based on energy method.But existing consideration
Drum have ignored nonlinear contact rigidity, finite element amendment MATRIX STIFFNESS, extension to the gear pair meshing characteristic analysis method of correction of the flank shape
The influence of engagement, it is impossible to which the accurate elastic deformation for calculating the gear teeth, the resultant error with FEM calculation is larger, it is impossible to true
Reflect the meshing characteristic of gear pair.
Therefore, not only modeling process is complicated to the gear pair meshing characteristic analysis method of correction of the flank shape for consideration drum of the prior art
And it is heavy, computational efficiency is low, requires higher to computing power, and have ignored nonlinear contact rigidity, finite element amendment
MATRIX STIFFNESS, the influence for extending engagement, it is impossible to the accurate elastic deformation for calculating the gear teeth, the resultant error with FEM calculation
It is larger, it is impossible to the meshing characteristic of true reflection gear pair.
The content of the invention
(1) technical problem to be solved
For existing technical problem, it is special that the present invention proposes that a kind of consideration drum of amendment is engaged to the gear pair of correction of the flank shape
Property analysis method, it is complicated and heavy to solve modeling process of the prior art, and computational efficiency is low, to computing power requirement
Higher, the resultant error of calculating is larger, it is impossible to truly the problems such as the meshing characteristic of reflection gear pair.
(2) technical scheme
In order to achieve the above object, the main technical schemes that the present invention is used include：
A kind of consideration drum of amendment comprises the following steps to the gear pair meshing characteristic analysis method of correction of the flank shape：
S1：Obtain the basic parameter of gear pair and rouse to profile modifying parameters；
S2：Based on gear pair total profile deviation, set up and consider nonlinear contact, finite element amendment MATRIX STIFFNESS, extension engagement
The drum of influence is to the secondary mesh stiffness computation model of profile modifying gear；
S2.1：Along facewidth Directional Decomposition it is N number of independent and uniform web gear by the gear teeth of gear pair, L represents the facewidth,
N represents total thin slice number, as shown in Figure 2.Calculate the total profile deviation in each position of engagement per plate sheet gear；In Fig. 2 a and Fig. 2 c
In, dotted line represents drum to modification curve (circular curve), and each plate sheet gear-profile deviation can be expressed as：
En=Ep,n+Eg,n
(1)
In formula,Driving wheel and driven pulley are represented respectively
Total profile deviation；znCoordinate for each thin slice along facewidth direction；RpAnd RgRepresent that the drum of driving wheel and driven pulley is justified to modification curve
Arc radius, they can be expressed as：
In formula, L is the facewidth, as shown in Figure 3：cβIt is the profiling quantity of axial modification；
S2.2：It is firm using consideration nonlinear contact, finite element amendment matrix based on drum to the secondary total profile deviation of profile modifying gear
Degree, the gear pair meshing characteristic analysis method of extension engagement influence, calculate the time-variant mesh stiffness for obtaining every plate sheet gear pair
kn, so as to obtain maximum deformation quantity of the thin slice spur gear pair in engagement process：
In formula, F is total engagement force, QmFor maximum deformation quantity, n is natural number, and N is the web gear number decomposed, EnTo be each
Plate sheet gear-profile deviation, knFor the time-variant mesh stiffness of each plate sheet gear pair.To make QmResult of calculation is more accurate,
This method is by the way of iterating, knCalculated according to equation below and further substitute into formula (3)：
S2.3：According to maximum deformation quantity Q of the thin slice spur gear pair in engagement processm, calculate and obtain drum to profile modifying gear
The secondary time-variant mesh stiffness in each position of engagement of whole flank profil：
Consider to be expressed as follows to the spur gear pair engagement global stiffness of correction of the flank shape containing drum：
S3：Set up containing drum to the engaging tooth wheel set threedimensional model of correction of the flank shape, threedimensional model is imported into ANSYS softwares, set up
Three-dimensional finite element contact model, solves the time-variant mesh stiffness data in the whole engagement process of gear；
S3.1：Set up by three-dimensional drawing software Autodesk Inventor Professional (AIP) containing drum to repairing
The engaging tooth wheel set threedimensional model of shape, saves as " .sat " file that ANSYS can be recognized, and imported into ANSYS softwares；
S3.2：Contact type is defined, contact pair, selection solid element Solid185, osculating element Conta174 wounds is created
Contact pair is built, contact type is set to Standard contact, and contact stiffness coefficient is set to 1.0, and coefficient of friction is set to 0.2, it is considered to which extension is nibbled
Close effect and create 3 gear contacts pair, pass through ANSYS automatic identification contact conditions；
S3.3：Apply constraint, constrain all frees degree of driven gear endoporus boundary node, built at driving gear endoporus center
A node is found as main controlled node, driving gear endoporus boundary point and main controlled node are defined as a rigid region, constrained
The translational degree of freedom of main controlled node, retains its rotational freedom；
S3.4：Load is defined, applies tangential force F on all nodes in driving gear endoporus border and carrys out simulation torque：
In formula：T1For input torque, rint1For driving gear internal bore radius, n represents driving gear endoporus boundary node number,
LeFor effective working flank width.The a certain gear teeth of driven gear are just entered to the position of engagement as reference position, from this
It is a mesh cycle that position, which starts to enter the process of engagement to the next gear teeth of driven pulley,.In the process, driving wheel is turned over
AngleBy driving gear is turned in a mesh cycle angle bisecting into 120 parts, obtain 121 it is discrete
Angle position, is loaded to each discrete location.
S3.5：Processor is solved to solve the gear engagement model data of each position of engagement；
S3.6：Result is extracted in processing：The driving wheel corner deflection of each discrete location is extracted, is tried to achieve often according to formula 8
The mesh stiffness k of one discrete location, so as to obtain the time-variant mesh stiffness in the whole engagement process of gear；
In formula, T1The moment of torsion suffered by gear, Δ θ is the corner deflection of gear, rb1For driving gear base radius；
S4：Root-mean-square error based on analytical Calculation result and finite element solving result：
In formula, λ is the independent variable of error function；kA-AMAnd kB-AMIt is analytical Calculation result respectively in bidentate class mark position A
With monodentate class mark position B mesh stiffness；
kA-FEMAnd kB-FEMIt is that finite element solving result is firm in bidentate class mark position A and monodentate class mark position B engagement
Degree；
With the minimum target of root-mean-square error, different drums are obtained to profiling quantity cβTime-variant mesh stiffness analytic method it is firm
Spend correction factor λk, λ is tried to achieve using quadratic function approximating methodkAnd cβBetween relational expression：
In formula, a, b, c are the coefficient of quadratic equation；
S5：Any drum is given to profiling quantity cβ, gear pair time-variant mesh stiffness K is calculated by S2T, pass through the calculating pair of formula 8
The correction factor λ answeredk, obtain accurate time-variant mesh stiffness result K=λk·KT, further obtain time-variant mesh stiffness curve
Figure.
(3) beneficial effect
The beneficial effects of the invention are as follows：The consideration drum for the amendment that the present invention is provided is analyzed to the gear pair meshing characteristic of correction of the flank shape
Method, modeling process is simple, and amount of calculation is small, requires relatively low to computing power, and take into account nonlinear contact rigidity, have
Limit member amendment MATRIX STIFFNESS, the influence for extending engagement, therefore, it is possible to the accurate elastic deformation for calculating the gear teeth, while with it is limited
The resultant error that member is calculated is small, can truly reflect the meshing characteristic of gear pair.
Brief description of the drawings
Fig. 1 rouses the gear pair meshing characteristic analysis method to correction of the flank shape for the consideration of the amendment in the specific embodiment of the invention
Flow chart；
Fig. 2 rouses the model of gear schematic diagram to correction of the flank shape for the consideration in the specific embodiment of the invention, wherein, (a) is represented
The whole gear teeth, (b) is the gear thin slice after discrete, and (c) is to rouse to modification curve schematic diagram；
Fig. 3 is the structural representation of driving gear in the specific embodiment of the invention；
Fig. 4 is drum in the specific embodiment of the invention to profiling quantity cβRespectively 0 μm, 5 μm, 10 μm, 15 μm, 20 μm
Gear time-variant mesh stiffness is parsed and result of finite element, wherein, (a) represents analysis result, and (b) represents finite element result；
Fig. 5 is that the use quadratic function approximating method in the specific embodiment of the invention is fitted obtained stiffness modification
Curve；
Fig. 6 is (c under any given profiling quantity in the specific embodiment of the inventionβ=2.5 μm, 7.5 μm, 12.5 μm and
17.5 μm), calculated using finite element method and gear pair meshing characteristic analysis method meter of the drum to correction of the flank shape is considered using amendment
Obtained time-variant mesh stiffness curve comparison figure, wherein (a) represents analysis result, (b) represents finite element result.
Embodiment
In order to preferably explain the present invention, in order to understand, below in conjunction with the accompanying drawings, by embodiment, to this hair
It is bright to be described in detail.
As shown in Figure 1：Roused present embodiment discloses a kind of consideration of amendment to the gear pair meshing characteristic analysis side of correction of the flank shape
Method, comprises the following steps：
S1：Obtain the basic parameter of gear pair and rouse to profile modifying parameters；
In the present embodiment, the basic parameter and drum for obtaining gear pair are as shown in table 1 to profile modifying parameters：
Table 1 is roused to the secondary basic parameter of profile modifying gear
In the present embodiment, drum is 0~20 μm to profiling quantity, and expects in the range of quick be somebody's turn to do any drum to profiling quantity
The time-variant mesh stiffness of lower tooth wheel set.
S2：Based on gear pair tooth profile error, set up and consider nonlinear contact, finite element amendment MATRIX STIFFNESS, extension engagement
The drum of influence is to the secondary mesh stiffness computation model of profile modifying gear；
S2.1：Drum is chosen to profile modifying parameters cβFor 0 μm, 5 μm, 10 μm, 15 μm, 20 μm, by the gear teeth of gear pair along the facewidth
Directional Decomposition is 40 independences and uniform web gear.Calculated according to formula (1)~(2) per plate sheet gear in each engagement
The total profile deviation E of positionn；
S2.2：It is firm using consideration nonlinear contact, finite element amendment matrix based on drum to the secondary total profile deviation of profile modifying gear
Degree, the gear pair meshing characteristic analysis method of extension engagement influence, calculate the time-variant mesh stiffness for obtaining every plate sheet gear pair
kn, so as to obtain maximum deformation quantity Q of the thin slice spur gear pair in engagement processm；By the way of iterating, according to formula
(4) k is calculatednAnd formula (3) is further substituted into, so as to obtain more accurate Qm；
S2.3：According to maximum deformation quantity Q of the thin slice spur gear pair in engagement processm, calculated by formula (5) or (6)
Obtain drum to profile modifying gear pair each position of engagement of whole flank profil time-variant mesh stiffness KT, stiffness curve is as shown in fig. 4 a；
S3：The engaging tooth wheel set threedimensional model to correction of the flank shape containing drum is set up, driving wheel threedimensional model is as shown in figure 3, by three-dimensional
Model imported into ANSYS softwares, sets up three-dimensional finite element contact model, and the time-varying engagement solved in the whole engagement process of gear is firm
Degrees of data, finite element solving result is as shown in Figure 4 b；
Specifically, S3.1：Built respectively by three-dimensional drawing software Autodesk Inventor Professional (AIP)
The vertical drum that contains is to profiling quantity cβFor 0 μm, 5 μm, 10 μm, 15 μm, 20 μm when engaging tooth wheel set threedimensional model, saving as ANSYS can
With " .sat " file of identification, and it is directed respectively into ANSYS softwares；
S3.2：Contact type is defined, contact pair, selection solid element Solid185, osculating element Conta174 wounds is created
Contact pair is built, contact type is set to Standard contact, and contact stiffness coefficient is set to 1.0, and coefficient of friction is set to 0.2, it is considered to which extension is nibbled
Close effect and create 3 gear contacts pair, pass through ANSYS automatic identification contact conditions.
S3.3：Apply constraint, constrain all frees degree of driven gear endoporus boundary node, built at driving gear endoporus center
A node is found as main controlled node, driving gear endoporus boundary point and main controlled node are defined as a rigid region, constrained
The translational degree of freedom of main controlled node, retains its rotational freedom.
S3.4：Load is defined, applies tangential force F (being calculated by formula 7) on all nodes in driving gear endoporus border
Carry out simulation torque, using a certain gear teeth of driven gear just enter engagement position as reference position, since this position to
It is a mesh cycle that the next gear teeth of driven pulley, which enter the process of engagement,.In the process, the angle that driving wheel is turned overBy driving gear is turned in a mesh cycle angle bisecting into 120 parts, 121 discrete angles are obtained
Position, is loaded to each discrete location；
S3.5：Processor is solved to solve the gear engagement model data of each position of engagement；
S3.6：Result is extracted in processing, is extracted the driving wheel corner deflection of each discrete location, is tried to achieve according to formula (8)
The mesh stiffness k of each discrete location, so as to obtain the time-variant mesh stiffness in the whole engagement process of gear；
S4：Based on analytical Calculation result and finite element solving result in bidentate class mark position A and monodentate class mark position B
Mesh stiffness, as shown in table 2, root-mean-square error function representation is：
In formula, λ is the independent variable of error function；kA-AMAnd kB-AMIt is analytical Calculation result respectively in bidentate class mark position A
With monodentate class mark position B mesh stiffness；kA-FEMAnd kB-FEMIt is finite element solving result in bidentate class mark position A and list
Tooth class mark position B mesh stiffness.
Using root-mean-square error minimum value as target, different drums are obtained to profiling quantity cβTime-variant mesh stiffness analytic method
Stiffness modification λk(being shown in Table 2) tries to achieve λ using quadratic function approximating methodkAnd cβBetween relational expression：
In formula, the coefficient of quadratic equation is respectively a=5.065 × 10-4, b=-1.255 × 10-3, c=0.9954, fitting
Curve is shown in Fig. 5.
Analytic method and finite element method calculate obtained time-variant mesh stiffness at the single, double tooth class mark of table 2 and rigidity is repaiied
Positive coefficient
S5：Any drum is given to profiling quantity cβ=2.5 μm, 7.5 μm, 12.5 μm and 17.5 μm, gear pair is calculated by S2
Time-variant mesh stiffness KT, corresponding correction factor λ is calculated by formula 8k, then can obtain accurate time-variant mesh stiffness result K=
λk·KT, obtain time-variant mesh stiffness curve map, such as Fig. 6 a, the error of the modification method and finite element method as shown in table 3, most
Big error is only 2.1%.
Time-variant mesh stiffness is contrasted with finite element method before and after the analytic modell analytical model amendment of table 3
From the present embodiment it can be seen that the consideration drum of the amendment of the offer of the present invention divides to the gear pair meshing characteristic of correction of the flank shape
Analysis method, modeling process is simple, and amount of calculation is small, requires relatively low to computing power, and firm in view of nonlinear contact of knowing clearly
Degree, finite element amendment MATRIX STIFFNESS, the influence for extending engagement, therefore, it is possible to accurately calculate the elastic deformation of the gear teeth, simultaneously
Resultant error with FEM calculation is small, can truly reflect the meshing characteristic of gear pair.
The technical principle of the present invention is described above in association with specific embodiment, these descriptions are intended merely to explain the present invention's
Principle, it is impossible to be construed to limiting the scope of the invention in any way.Based on explaining herein, those skilled in the art
Would not require any inventive effort can associate other embodiments of the present invention, and these modes fall within this hair
Within bright protection domain.
Claims (10)
1. the gear pair meshing characteristic analysis method to correction of the flank shape is roused in a kind of consideration of amendment, it is characterised in that comprised the following steps：
S1：Obtain the basic parameter of gear pair and rouse to profile modifying parameters；
S2：Based on gear pair total profile deviation, set up and consider nonlinear contact, finite element amendment MATRIX STIFFNESS, extension engagement influence
Drum to the secondary mesh stiffness computation model of profile modifying gear；
S3：Engaging tooth wheel set threedimensional model containing from drum to correction of the flank shape is set up by three-dimensional drawing simulation softward, and threedimensional model is led
Enter to ANSYS softwares and set up three-dimensional finite element contact model, solve the time-variant mesh stiffness data in the whole engagement process of gear；
S4：Different drums are obtained to profiling quantity cβTime-variant mesh stiffness analytic method correction factor λk, using quadratic interpolation method
Try to achieve λkAnd cβBetween relational expression；
S5：Any drum is given to profiling quantity cβ, calculate gear pair time-variant mesh stiffness KTAnd corresponding correction factor λk, obtain essence
True time-variant mesh stiffness result K=λk·KT, obtain time-variant mesh stiffness curve map.
2. the consideration drum of amendment according to claim 1 exists to the gear pair meshing characteristic analysis method of correction of the flank shape, its feature
In the step S2 also includes：
S2.1：Along facewidth Directional Decomposition it is N number of independent and uniform web gear by the gear teeth of gear pair, and calculates per plate sheet
Tooth profile error of the gear in each position of engagement；
S2.2：The gear pair meshing characteristic influenceed using nonlinear contact, finite element amendment MATRIX STIFFNESS, extension engagement is considered divides
Analysis method, calculates the time-variant mesh stiffness k for obtaining every plate sheet gear pairn；
S2.3：On the basis of all web gear pairs are in engagement, calculating obtains drum to profile modifying gear pair in whole tooth
The time-variant mesh stiffness of wide each position of engagement.
3. the consideration drum of amendment according to claim 2 exists to the gear pair meshing characteristic analysis method of correction of the flank shape, its feature
In each plate sheet gear-profile deviation E in methods describednIt can be expressed as:
En=Ep,n+Eg,n
EnFor each plate sheet gear-profile deviation, EpAnd EgThe respectively total profile deviation of driving wheel and driven pulley, n is natural number.
4. the consideration drum of amendment according to claim 1 exists to the gear pair meshing characteristic analysis method of correction of the flank shape, its feature
In the step S3 also includes：
S3.1：Set up by three-dimensional drawing software Autodesk Inventor Professional (AIP) containing bulging to correction of the flank shape
Engaging tooth wheel set threedimensional model；
S3.2：Contact type is defined, contact pair is created, selection solid element Solid185, osculating element Conta174 are created and connect
Tactile pair, contact type is set to Standard contact, and contact stiffness coefficient is set to 1.0, and coefficient of friction is set to 0.2, it is considered to extension engagement effect
3 gear contacts pair should be created, pass through ANSYS automatic identification contact conditions；
S3.3：Apply constraint, constrain all frees degree of driven gear endoporus boundary node, one is set up at driving gear endoporus center
Driving gear endoporus boundary point and main controlled node are defined as a rigid region by individual node as main controlled node, constrain master control
The translational degree of freedom of node, retains its rotational freedom；
S3.4：Load is defined, applies tangential force F on all nodes in driving gear endoporus border and carrys out simulation torque：
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<mi>F</mi>
<mo>=</mo>
<mfrac>
<msub>
<mi>T</mi>
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</msub>
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<mi>L</mi>
<mi>e</mi>
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</mrow>
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In formula：T1For input torque, rint1For driving gear internal bore radius, n represents driving gear endoporus boundary node number, LeFor
Effective working flank width；
S3.5：Processor is solved to solve the gear engagement model data of each position of engagement；
S3.6：Result is extracted in processing, the driving wheel corner deflection of each discrete location is extracted, according to formulaTry to achieve
The mesh stiffness k of each discrete location, obtains the time-variant mesh stiffness data in the whole engagement process of gear；
In formula, T1The moment of torsion suffered by gear, Δ θ is the corner deflection of gear, rb1For driving gear base radius.
5. the consideration drum of amendment according to claim 2 exists to the gear pair meshing characteristic analysis method of correction of the flank shape, its feature
In calculating obtains the time-variant mesh stiffness k of every plate sheet gear pair in methods describedn, thus obtain thin slice spur gear pair and nibbling
Maximum deformation quantity Q during conjunctionmFor：
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<mi>Q</mi>
<mi>m</mi>
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In formula, F is total engagement force, QmFor maximum deformation quantity, n is natural number, and N is the web gear number decomposed, EnFor per a piece of thin
Plate gear total profile deviation, knFor the time-variant mesh stiffness of each plate sheet gear pair.
6. the consideration drum of amendment according to claim 5 exists to the gear pair meshing characteristic analysis method of correction of the flank shape, its feature
In methods described also includes：To make QmResult of calculation is more accurate, and Q is tried to achieve by the way of iteratingm, knCalculation formula
It is as follows：
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In formula, knFor the time-variant mesh stiffness of each plate sheet gear pair, QmFor maximum deformation quantity, knFor each plate sheet gear
Secondary time-variant mesh stiffness, EnFor every plate sheet gear-profile deviation, θ represents the corner in Meshing Process of Spur Gear, reflects gear
Change in location in engagement process, i.e. kn(θ) represents the rigidity at the θ of the position of engagement.
7. the consideration drum of amendment according to claim 2 exists to the gear pair meshing characteristic analysis method of correction of the flank shape, its feature
In the drum is to time-variant mesh stiffness KT of the profile modifying gear pair in each position of engagement of whole flank profil：
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It is described to consider to be expressed as follows to the spur gear pair engagement global stiffness of correction of the flank shape containing drum：
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</mrow>
In formula, QmFor maximum deformation quantity, KTEngaged for drum to time-varying of the profile modifying gear pair in each position of engagement of whole flank profil firm
Degree, F is total engagement force, QmFor maximum deformation quantity, n is natural number, and N is the web gear number decomposed, EnFor each plate sheet gear
Total profile deviation, knFor the time-variant mesh stiffness of each plate sheet gear pair.
8. the consideration drum of amendment according to claim 1 exists to the gear pair meshing characteristic analysis method of correction of the flank shape, its feature
In analytical Calculation result and the root-mean-square error function obtained by finite element solving result are in step S4：
In formula, λ is the independent variable of error function, kA-AMAnd kB-AMIt is analytical Calculation result respectively in bidentate class mark position A and list
Tooth class mark position B mesh stiffness, kA-FEMAnd kB-FEMIt is finite element solving result respectively in bidentate class mark position A and list
Tooth class mark position B mesh stiffness.
9. the consideration drum of amendment according to claim 1 exists to the gear pair meshing characteristic analysis method of correction of the flank shape, its feature
In calculating obtains different drums to profiling quantity cβTime-variant mesh stiffness analytic method stiffness modification λk, using quadratic function
Approximating method tries to achieve λkAnd cβBetween relational expression：
<mrow>
<msub>
<mi>&lambda;</mi>
<mi>k</mi>
</msub>
<mo>=</mo>
<msubsup>
<mi>ac</mi>
<mi>&beta;</mi>
<mn>2</mn>
</msubsup>
<mo>+</mo>
<msub>
<mi>bc</mi>
<mi>&beta;</mi>
</msub>
<mo>+</mo>
<mi>c</mi>
</mrow>
In formula, a, b, c are the coefficient of quadratic equation.
10. the consideration drum of amendment according to claim 1 exists to the gear pair meshing characteristic analysis method of correction of the flank shape, its feature
In,
Pass through formula K=λk·KTObtain accurate time-variant mesh stiffness data；
According to obtained accurate time-variant mesh stiffness data, obtain and accurately consider that drum is engaged just to the secondary time-varying of profile modifying gear
Write music line chart.
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Application publication date: 20170912 Assignee: JIANGSU JINXIANG TRANSMISSION EQUIPMENT Co.,Ltd. Assignor: Northeastern University Contract record no.: X2020210000037 Denomination of invention: A modified meshing characteristic analysis method of gear pair considering drum modification Granted publication date: 20190719 License type: Common License Record date: 20201223 |
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