# The Analysis and Modeling of the Synthetical Meshing Stiffness of Inner Gearing considering the Flexible Inner Ring Gear

Authors: Shengyang Hu; Zongde Fang
Journal: Shock and Vibration
 (2019)

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## Abstract

As a key part of vibration generation and transmission of planetary gear transmissions, thin-walled inner ring gear deforms under the influence of meshing excitation and seriously affects the reliability and fatigue life of the transmission system. The effect of the flexibility of the inner ring gear on the transmission system is ignored in the calculation of making the inner ring gear as a rigid body in the lumped parameter model, while the calculation amount of the finite element model is too large. Therefore, it is very important to establish an accurate and reasonable model to solve the flexibility of the inner ring gear. In this paper, according to the supporting mode, supporting quantity, thickness, and sectional shape of the inner ring gear, the inner ring gear is reasonably separated into the form of multisection curved beam. The displacement of the gear teeth in the meshing line caused by the flexibility of the inner ring gear is obtained rapidly and accurately. It lays an important theoretical foundation for the dynamic analysis of planetary gear transmission.


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## Body

## 1. Introduction

The inner ring gear is a key component for the generation and transmission of planetary gear system vibration. In order to reduce the transmission weight and reduce the system vibration and noise, the inner ring gear [1, 2] and the elastic connection mode [3] are mostly adopted in the planetary gear transmission system to prevent the vibration of the planetary gear transmission system from being transmitted to the body. The vibration behavior of thin-walled inner ring gear is very complicated due to the complex working condition and the influence of meshing excitation, so its reliability and fatigue life are seriously affected. Therefore, it is of great significance to analyze the flexibility of inner ring gear to reveal the dynamic performance of the system and to design a planetary transmission device with light, low vibration, and high reliability. Some scholars [4–7] used the lumped mass method to establish the dynamic model of the spur gear planetary gear system, which included the flexibility of inner ring gear, and analyzed its inherent characteristics. Chen’s [8, 9] theoretical model of nonlinear excitation of meshing stiffness about flexible ring gear reveals the deformation of inner ring gear under nonlinear large deformation. However, the solution model of the elastic deformation of the inner ring gear under linear conditions is not given.Through analyzing the existing lumped parameter model and finite element model, the lumped parameter model fails to take into account the elastic deformation of transmission components, especially the flexible inner ring gear, so the analysis accuracy still needs to be improved. In contrast, the finite element model can accurately reflect the load condition of the planetary transmission system by taking into account the elastic deformation of each component. However, the disadvantage of this model is that the modeling process is complex, the degree of freedom of the model is large, and the solution is time-consuming. Therefore, in this paper, the inner ring gear is considered to be composed of matrix and gear teeth. The overall meshing stiffness of the inner gearing teeth is obtained by LTCA, while the flexural deformation of the inner ring gear is simulated by the curved beam model to obtain the amount of displacement generated by normal meshing force and the rigidity on the meshing line caused by the flexibility of the inner ring gear. Because the curved beam is close to the flexible inner ring gear on the geometric model, it can reduce the number of sections and calculation and is more accurate than the straight beam model. By analyzing the different supporting modes of the flexibility of inner ring gear and combining with the boundary conditions of the corresponding curved beam, the corresponding formulas of bending, bending angle, and torsion angle are derived, and thus, the comprehensive deformation displacement of the meshing line of the flexible inner ring gear due to torsional angle deformation, bending deformation, and shear deformation is obtained. This model provides an important basis for accurate dynamic analysis of the planetary transmission system.


## 2. Analysis of Flexible Deformation of Inner Ring Gear

This paper mainly studies the calculation method of inner ring gear deformation under two supporting modes (fixed support and pin support). Assuming that the inner ring gear hasn supports, the inner ring gear can be divided into curved beams [10] that are uniformly curved at least n segments (Figure 1).Figure 1
Schematic diagram of pin support in inner ring gear.Setting of boundary conditions for supporting mode:(1)
Bolt connection is usually used for the inner ring gear with fixed support. The translational displacement of the beam at the support position is completely constrained, and only the rotational degree of freedom is retained, that is,u=0;ω=0;θ1=θ2.(2)
There are two kinds of boundary conditions for the pin supported inner ring gear. When the beam is far away from the center of the circle along the radial direction, it will be in contact with the pin. The circumferential displacement and radial displacement of the beam at the support position are completely restrained. At this point, the boundary condition is the same as the fixed mode, namely,u=0;ω=0;θ1=θ2. When the beam moves along the radial direction close to the center of the circle, it will be separated by contact with the pin. The circumferential displacement and radial displacement of the beam at the support position can be carried out simultaneously. At this point, the boundary condition is u1=u2;ω1=ω2;θ1=θ2.Based on the above analysis, the corresponding deformation, internal force, and torque can be obtained by setting different boundary conditions for arbitrary boundary constraint positions of any section of the curved beam, thus laying a foundation for the calculation of meshing stiffness of inner ring gear. The supporting mode of this paper is pin connection, and its boundary condition is the first mode according to the actual situation.When calculating the influence of inner ring gear deformation on meshing stiffness, the inner gear teeth are treated as a rigid body, and the meshing force acts on the inner ring gear in the form of circumferential force, radial force, and torque. The relation is(1)Fr=Fncosα,Ft=Fnsinα,m0=FtOB−FrAB.The circumferential displacement, radial displacement, and bending angle of the inner ring gear are obtained by transforming the obtained circumferential force and radial force into distributed force, and the displacement of the contact point on the tooth profile caused by the inner ring gear deformation on the line of action is obtained as(2)σ=ωcosα+μsinα+θOAsinβ.


## 3. Theory of Curved Beam

Two fourth-order simultaneous differential equations are usually needed to solve the internal force deformation of a curved beam. In this case, a series of linear equations determined by boundary conditions are solved by solving multiple integral constants. This will make the calculation work complicated, and when the boundary conditions change and the load moves, the closed solution is used to solve the general differential equation to calculate the deformation and internal force of the curved beam.


### 3.1. Load and Torque Is Applied in a Concentrated Way

This study mainly focuses on the influence of the flexible inner ring gear on the inner gearing stiffness. The inner ring gear is simplified into a smooth ring. According to the support boundary condition, the ring is divided into several sections, each section is regarded as a uniformly curved beam, and the deformation of the whole ring can be solved according to the boundary condition. When an external force acts on the tooth profile along the line of action, the displacement of the meshing point caused by the deformation of the flexible ring on the line of action is superimposed with the displacement of the meshing point caused by the deformation of the tooth. The ratio of force to total displacement is the synthetical stiffness of flexible inner ring gear.The expressions of strain, curvature, and torsion rate can be obtained by analyzing uniformly curved beams. In accordance with the principle of general elastomer material mechanics, the following basic differential equation can be established by linking the internal force and deformation of the section:(3)Mx=−EIxd2ωdz2−ϕr,T=−EIωd3ϕdz3+1rd3ωdz3+GIddϕdz+1rdωdz,dMdφz=−T−rQ,where A is the cross-sectional area of the beam; E is the modulus of elasticity; G is the shear modulus; Ix and Iy correspond to the bending moment of inertia about the x and y axes; Id is the torsional moment of inertia about the z axis; Iω is the warp constant of the beam; Q is the shear.Through the derivation and transformation of the above formula, the differential equation of bending and the corresponding expression of torsional angle and bending angle are obtained. According to formula (4), the relation between internal force and deformation of section is derived. The simple torsion theoretical equation with omitted section warping is established as follows (the shear deformation is minor, which is ignored here):(4)d3ωdφz3+dωdφz=r3EI1+kT+rQ,ϕ=1rd2ωdφz2+rEIM,θ=dωdz=1rdωdφz,where z=rφz and k=EI/GId.When the concentrated load and torque is applied to any position of the beam, the internal force of each section of the beam is divided into two parts.As shown in Figure2, when the concentrated load P and concentrated torque T act on any position φp of the beam, the internal force of each section of the beam is determined by equations (5) and (6):Figure 2
Calculation of deformation under concentrated loadP and concentrated torque T.When0≤φz≤φp,(5)Mzp=pr+Tsinφ0−φpsinφ0sinφz,Tzp=pr1−φpφ0−sinφ0−φpsinφ0cosφz−Tsinφ0−φpsinφ0cosφz,Qzp=−p1−φpφ0.Whenφp≤φz≤φ0,(6)Mzp=pr+Tsinφpsinφ0sinφ0−φz,Tzp=prsinφpsinφ0sinφ0−φz−φpφ0+Tsinφpsinφ0sinφ0−φz,Qzp=pφpφ0.Taking the load point as the boundary, the curved beam is divided into two sections,φz<φp and φz>φp, and the deflection differential equation obtained from above is(7)d3ω1dφz3+dω1dφz=pr3EI1−φpφ0−sinφ0−φpsinφpcosφz−1−φpφ0−Tr2EI1+ksinφ0−φpsinφpcosφz,(8)d3ω2dφz3+dω2dφz=pr3EI1+ksinφpsinφ0cosφ0−φz−kφpφ0+Tr2EI1+ksinφpsinφ0cosφ0−φz.The general solution of equations (7) and (8) is obtained as(9)ω1=A+Bsinφz+Ccosφz+pr3+Tr2EI∗1+k2sinφ0−φpsinφ0φzcosφz+pr3EIk1−φpφ0φz,ω2=D+Esinφz+Fcosφz−pr3+Tr2EI∗1+k2sinφpsinφ0φzcosφ0−φz−pr3EIkφpφ0φz.The solution is based on the following boundary conditions and continuous conditions:(1)
φz=0:ω1=0 or ω1″=0(2)
φz=φp:ω1=ω2,ω1′=ω2′, and ω1″=ω2″(3)
φz=φp:ω2=0 and ω2″=0The correlation coefficient is obtained by introducing boundary and continuous conditions:(10)A=0,C=0,B=pr3+Tr22EI1+kφ0sinφp−φpcosφ0−φpsinφpsin2φp−pr32EI1+3ksinφ0−φpsinφ0−Tr22EI1+ksinφ0−φpsinφ0,D=pr3EIkφp,E=pr32EI1+kφ0sinφpsin2φ0−1+kφpcosφpcotφ0+1+3ksinφpcotφ0+Tr22EI1+ktanϕ0φ0sinφpsinφ0cosφ0−φp+sinφp,F=pr32EI1+kφpcosφp−1+3ksinφp+Tr22EI1+kφpcosφp−sinφp.The obtained constants are substituted into the formula, and the bending of the curved beam under the action of concentrated load and concentrated torque and the corresponding formula of angle of bending and torsion are as follows:When0≤φz≤φp,(11)ω1=pr32EI1+ksinφ0φ0sinφpsinφ0sinφz−φpcosφ0−φpsinφz+φzsinφ0−φpcosφz−1+3ksinφ0−φpsinφ0sinφz+2k1−φpφ0φz+Tr22EI1+ksinφ0φ0sinφpsinφ0sinφz−φpcosφ0−φpsinφz+φzsinφ0−φpcosφz−sinφ0−φpcosφz,θ1=1rdω1dφz=pr22EI1+ksinφ0φ0sinφpsinφ0cosφz−φpcosφ0−φpcosφz−φzsinφ0−φpsinφz−2ksinφ0−φpsinφ0cosφz−1+φpφ0+TrEI1+k2sinφ0φ0sinφpsinφ0cosφz−φpcosφ0−φpcosφz−φzsinφ0−φpsinφz,φ1=1rd2ω1dφz2+rMEI=pr22EI1+ksinφ0φpcosφ0−φpsinφz−φ0sinφpsinφ0sinφz−sinφ0−φpφzcosφz−sinφz+TrEI1+k2sinφ0φpcosφ0−φpsinφz−φ0sinφpsinφ0sinφz−sinφ0−φpφzcosφz−sinφz−ksinφpsinφ0sinφ0−φp.Whenϕp≤ϕz≤ϕ0,(12)ω2=pr32EI1+ksinφ0φ0sinφpsinφ0sinφz+φpsinφ0−φpcosφp−φzcosφ0−φpcosφp−1+3ksinφ0−φzsinφ0sinφp+2kφp1−φzφ0+Tr2EI1+k2sinφ0φ0sinφpsinφ0sinφz+φpsinφ0−φpcosφp−φzcosφ0−φpsinφp−sinφpsinφ0−φz,θ2=1rdω2dφz=pr22EI1+ksinφ0φ0sinφpsinφ0cosφz−φpcosφ0−φzcosφp−φzsinφ0−φzsinφp+2kcosφ0−φzsinφ0sinφp−φpφ0+TrEI1+k2sinφ0φ0sinφpsinφ0cosφz−φpcosφ0−φzcosφp−φzsinφ0−φzsinφp,φ2=1rd2ω2dϕz2+rMEI=pr22EI1+ksinφ0φzcosφ0−φzsinφp−φ0sinφpsinφ0sinϕz−sinφ0−φzφpcosφp−sinφp+pr22EI1+ksinφ0φzcosφ0−φzsinφp−φ0sinφpsinφ0sinφz−sinφ0−φzφpcosφp−sinφp+TrEI1+k2sinφ0φzcosφ0−φzsinφp−φ0sinφpsinφ0sinφz−sinφ0−φzφpcosφp−sinφp−ksinφ0−φzsinφ0sinφp.By establishing the above theoretical analytical formulas, the deformation of curved beams under different loads at different positions was calculated easily and quickly, which provided an important theoretical basis for the relevant theoretical analysis. At the same time, it also provides important theoretical support for the solution of the influence of flexible inner ring gear on the synthetical stiffness.


### 3.2. Comparison and Verification with Finite Element Method

In the finite element software ABAQUS, the circular curved beam structure was established, and the density of the model was set as 7.85e − 9 kg/mm3, the elastic modulus was 2.06e + 5 GPa, and the shear modulus was 7.938e + 4 GPa. The beam element type B21 is adopted, and the section shape and size of the beam is set (rectangular section with thickness of 20 mm and tooth width of 50 mm). At the same time, it is divided into n sections (5 sections in this paper), and different coordinate systems are set at the splitting points, so as to set different boundary conditions through the splitting points. According to the above, its deformation in different directions is obtained, and its radial displacement (bending), bending angle, and torsion angle are obtained. There is an order of magnitude difference between shear deformation and deflection bending due to shear. Therefore, we can ignore its influence and obtain the following theory and finite element comparison.It can be seen from the comparison of the above Figures3 and 4 that the formula based on the structural mechanics theory and the finite element model are highly consistent with the bending and bending angle of the curved beam. It is verified that the formula established in the theoretical analysis is reasonable and accurate, which can quickly and accurately obtain the bending of the curved beam, thus providing a solid theoretical foundation for calculating the flexible deformation of the inner ring gear. Meanwhile, the stress and deformation of the inner ring gear are analyzed in the first part of this paper. The related displacement derived from the theory and the transfer of meshing position caused by the bending angle of the inner ring gear circumferential are combined. The comprehensive deformation of the gear teeth caused by the flexibility of the inner ring gear is obtained, as shown in Figure 5.Figure 3
Comparison of bending of curved beams by two methods.Figure 4
Comparison of bending angle of curved beam by two methods.Figure 5
The overall deformation of the flexible inner ring gear is on the line of action.


## 3.1. Load and Torque Is Applied in a Concentrated Way

This study mainly focuses on the influence of the flexible inner ring gear on the inner gearing stiffness. The inner ring gear is simplified into a smooth ring. According to the support boundary condition, the ring is divided into several sections, each section is regarded as a uniformly curved beam, and the deformation of the whole ring can be solved according to the boundary condition. When an external force acts on the tooth profile along the line of action, the displacement of the meshing point caused by the deformation of the flexible ring on the line of action is superimposed with the displacement of the meshing point caused by the deformation of the tooth. The ratio of force to total displacement is the synthetical stiffness of flexible inner ring gear.The expressions of strain, curvature, and torsion rate can be obtained by analyzing uniformly curved beams. In accordance with the principle of general elastomer material mechanics, the following basic differential equation can be established by linking the internal force and deformation of the section:(3)Mx=−EIxd2ωdz2−ϕr,T=−EIωd3ϕdz3+1rd3ωdz3+GIddϕdz+1rdωdz,dMdφz=−T−rQ,where A is the cross-sectional area of the beam; E is the modulus of elasticity; G is the shear modulus; Ix and Iy correspond to the bending moment of inertia about the x and y axes; Id is the torsional moment of inertia about the z axis; Iω is the warp constant of the beam; Q is the shear.Through the derivation and transformation of the above formula, the differential equation of bending and the corresponding expression of torsional angle and bending angle are obtained. According to formula (4), the relation between internal force and deformation of section is derived. The simple torsion theoretical equation with omitted section warping is established as follows (the shear deformation is minor, which is ignored here):(4)d3ωdφz3+dωdφz=r3EI1+kT+rQ,ϕ=1rd2ωdφz2+rEIM,θ=dωdz=1rdωdφz,where z=rφz and k=EI/GId.When the concentrated load and torque is applied to any position of the beam, the internal force of each section of the beam is divided into two parts.As shown in Figure2, when the concentrated load P and concentrated torque T act on any position φp of the beam, the internal force of each section of the beam is determined by equations (5) and (6):Figure 2
Calculation of deformation under concentrated loadP and concentrated torque T.When0≤φz≤φp,(5)Mzp=pr+Tsinφ0−φpsinφ0sinφz,Tzp=pr1−φpφ0−sinφ0−φpsinφ0cosφz−Tsinφ0−φpsinφ0cosφz,Qzp=−p1−φpφ0.Whenφp≤φz≤φ0,(6)Mzp=pr+Tsinφpsinφ0sinφ0−φz,Tzp=prsinφpsinφ0sinφ0−φz−φpφ0+Tsinφpsinφ0sinφ0−φz,Qzp=pφpφ0.Taking the load point as the boundary, the curved beam is divided into two sections,φz<φp and φz>φp, and the deflection differential equation obtained from above is(7)d3ω1dφz3+dω1dφz=pr3EI1−φpφ0−sinφ0−φpsinφpcosφz−1−φpφ0−Tr2EI1+ksinφ0−φpsinφpcosφz,(8)d3ω2dφz3+dω2dφz=pr3EI1+ksinφpsinφ0cosφ0−φz−kφpφ0+Tr2EI1+ksinφpsinφ0cosφ0−φz.The general solution of equations (7) and (8) is obtained as(9)ω1=A+Bsinφz+Ccosφz+pr3+Tr2EI∗1+k2sinφ0−φpsinφ0φzcosφz+pr3EIk1−φpφ0φz,ω2=D+Esinφz+Fcosφz−pr3+Tr2EI∗1+k2sinφpsinφ0φzcosφ0−φz−pr3EIkφpφ0φz.The solution is based on the following boundary conditions and continuous conditions:(1)
φz=0:ω1=0 or ω1″=0(2)
φz=φp:ω1=ω2,ω1′=ω2′, and ω1″=ω2″(3)
φz=φp:ω2=0 and ω2″=0The correlation coefficient is obtained by introducing boundary and continuous conditions:(10)A=0,C=0,B=pr3+Tr22EI1+kφ0sinφp−φpcosφ0−φpsinφpsin2φp−pr32EI1+3ksinφ0−φpsinφ0−Tr22EI1+ksinφ0−φpsinφ0,D=pr3EIkφp,E=pr32EI1+kφ0sinφpsin2φ0−1+kφpcosφpcotφ0+1+3ksinφpcotφ0+Tr22EI1+ktanϕ0φ0sinφpsinφ0cosφ0−φp+sinφp,F=pr32EI1+kφpcosφp−1+3ksinφp+Tr22EI1+kφpcosφp−sinφp.The obtained constants are substituted into the formula, and the bending of the curved beam under the action of concentrated load and concentrated torque and the corresponding formula of angle of bending and torsion are as follows:When0≤φz≤φp,(11)ω1=pr32EI1+ksinφ0φ0sinφpsinφ0sinφz−φpcosφ0−φpsinφz+φzsinφ0−φpcosφz−1+3ksinφ0−φpsinφ0sinφz+2k1−φpφ0φz+Tr22EI1+ksinφ0φ0sinφpsinφ0sinφz−φpcosφ0−φpsinφz+φzsinφ0−φpcosφz−sinφ0−φpcosφz,θ1=1rdω1dφz=pr22EI1+ksinφ0φ0sinφpsinφ0cosφz−φpcosφ0−φpcosφz−φzsinφ0−φpsinφz−2ksinφ0−φpsinφ0cosφz−1+φpφ0+TrEI1+k2sinφ0φ0sinφpsinφ0cosφz−φpcosφ0−φpcosφz−φzsinφ0−φpsinφz,φ1=1rd2ω1dφz2+rMEI=pr22EI1+ksinφ0φpcosφ0−φpsinφz−φ0sinφpsinφ0sinφz−sinφ0−φpφzcosφz−sinφz+TrEI1+k2sinφ0φpcosφ0−φpsinφz−φ0sinφpsinφ0sinφz−sinφ0−φpφzcosφz−sinφz−ksinφpsinφ0sinφ0−φp.Whenϕp≤ϕz≤ϕ0,(12)ω2=pr32EI1+ksinφ0φ0sinφpsinφ0sinφz+φpsinφ0−φpcosφp−φzcosφ0−φpcosφp−1+3ksinφ0−φzsinφ0sinφp+2kφp1−φzφ0+Tr2EI1+k2sinφ0φ0sinφpsinφ0sinφz+φpsinφ0−φpcosφp−φzcosφ0−φpsinφp−sinφpsinφ0−φz,θ2=1rdω2dφz=pr22EI1+ksinφ0φ0sinφpsinφ0cosφz−φpcosφ0−φzcosφp−φzsinφ0−φzsinφp+2kcosφ0−φzsinφ0sinφp−φpφ0+TrEI1+k2sinφ0φ0sinφpsinφ0cosφz−φpcosφ0−φzcosφp−φzsinφ0−φzsinφp,φ2=1rd2ω2dϕz2+rMEI=pr22EI1+ksinφ0φzcosφ0−φzsinφp−φ0sinφpsinφ0sinϕz−sinφ0−φzφpcosφp−sinφp+pr22EI1+ksinφ0φzcosφ0−φzsinφp−φ0sinφpsinφ0sinφz−sinφ0−φzφpcosφp−sinφp+TrEI1+k2sinφ0φzcosφ0−φzsinφp−φ0sinφpsinφ0sinφz−sinφ0−φzφpcosφp−sinφp−ksinφ0−φzsinφ0sinφp.By establishing the above theoretical analytical formulas, the deformation of curved beams under different loads at different positions was calculated easily and quickly, which provided an important theoretical basis for the relevant theoretical analysis. At the same time, it also provides important theoretical support for the solution of the influence of flexible inner ring gear on the synthetical stiffness.


## 3.2. Comparison and Verification with Finite Element Method

In the finite element software ABAQUS, the circular curved beam structure was established, and the density of the model was set as 7.85e − 9 kg/mm3, the elastic modulus was 2.06e + 5 GPa, and the shear modulus was 7.938e + 4 GPa. The beam element type B21 is adopted, and the section shape and size of the beam is set (rectangular section with thickness of 20 mm and tooth width of 50 mm). At the same time, it is divided into n sections (5 sections in this paper), and different coordinate systems are set at the splitting points, so as to set different boundary conditions through the splitting points. According to the above, its deformation in different directions is obtained, and its radial displacement (bending), bending angle, and torsion angle are obtained. There is an order of magnitude difference between shear deformation and deflection bending due to shear. Therefore, we can ignore its influence and obtain the following theory and finite element comparison.It can be seen from the comparison of the above Figures3 and 4 that the formula based on the structural mechanics theory and the finite element model are highly consistent with the bending and bending angle of the curved beam. It is verified that the formula established in the theoretical analysis is reasonable and accurate, which can quickly and accurately obtain the bending of the curved beam, thus providing a solid theoretical foundation for calculating the flexible deformation of the inner ring gear. Meanwhile, the stress and deformation of the inner ring gear are analyzed in the first part of this paper. The related displacement derived from the theory and the transfer of meshing position caused by the bending angle of the inner ring gear circumferential are combined. The comprehensive deformation of the gear teeth caused by the flexibility of the inner ring gear is obtained, as shown in Figure 5.Figure 3
Comparison of bending of curved beams by two methods.Figure 4
Comparison of bending angle of curved beam by two methods.Figure 5
The overall deformation of the flexible inner ring gear is on the line of action.


## 4. Calculation of Inner Gearing Meshing Stiffness

The synthetical stiffnessk of inner gearing can be divided into two parts, namely, the stiffness kr caused by the flexibility of the inner ring gear and the meshing stiffness kc of the gear tooth of inner gearing (without considering the flexibility of the inner ring gear). There are two methods to calculate the time-varying meshing stiffness kc of the gear tooth of inner gearing [11]. Each one applies to a different situation. The LTCA method adopted in this paper can accurately obtain the meshing stiffness of gears. The LTCA method is used to calculate the normal displacement of each instantaneous discrete point after tooth deformation. At the same time, the method solves the discrete load at the discrete point of the instantaneous contact ellipse long axis and the normal clearance of the tooth surface at the discrete point of the instantaneous contact ellipse long axis after the tooth deformation. This method can accurately obtain the discrete time-varying meshing stiffness of gears at different meshing points, which is similar to the method of local slope mesh stiffness proposed by Cooley et al. [11]. The LTCA method is suitable for the calculation of the planetary transmission system. Table 1 is the helical gear parameters.Table 1
Helical gear parameters.
Parameters
Unit
Driving pinion
Driven gear
Tooth number,Z1 and Z2
—
20
80
Normal module,mn
mm
5
5
Normal pressure angle,αn
deg
20
20
Helix angle,βm
deg
20
20
Face width,B
mm
50
50
Addendum,ha
mm
5
5
Dedendum,hf
mm
6.75
6.75
Elastic modulus,E
GPa
210
Density,ρ
g/cm3
7.85
Speed,v
r/min
1500
Power
kw
400In this paper, LTCA (load tooth contact analysis) [12] is used to calculate the total meshing stiffness of gear teeth considering the installation error. The basic idea of gear tooth meshing stiffness calculation is through TCA (tooth contact analysis) [13, 14] and LTCA (load tooth contact analysis). By using the deformation coordination equation, force balance, and nonembedding conditions, the total normal contact deformation of the meshing tooth surface is obtained, and the comprehensive meshing stiffness of the gear tooth is obtained by conversion. Considering the gear tooth, surface error resulted in the manufacturing process of impact load gear shaft torsional deformation and additional flexibility matrix effect on tooth surface composite flexibility matrix and the installation error and the effects of tooth surface modification, thus can accurately calculate the tooth mesh stiffness. Figure 6 is the flow chart based on the method of LTCA to calculate the integrated meshing stiffness.Figure 6
Flow chart for calculating the integrated meshing stiffness.


### 4.1. Deformation Coordination Equation

Suppose there are two pairs of gear tooth I and II meshing at the same time. The load tooth contact analysis model shown in Figure7 shows the cross section of the tooth flank along the long axis of the contact ellipse. i is the center of instantaneous contact ellipse on the tooth pair, j is the discrete point along the long axis on the tooth pair, and w is the initial pitch before contact on the tooth pair.Figure 7
The model of helical gear LTCA.Before gear deformation, the teeth of I and II tooth surface initial clearance are(13)wk=δk+bk,k=I,II,(14)wk=w1,w2,…,wi,…,wnT,(15)bk=b1,b2,…,bi,…,bnT,(16)δk=δ1,1,…,1,…,1T,(17)bM0=x1−x22+y1−y22+z1−z22,where n is the number of discrete points on the long axis of the instantaneous contact ellipse. bj (j = 1, 2, …, n) is the tooth surface normal clearance at the discrete point j of the long axis of the instantaneous contact ellipse. δ is the transmission error of gear pair k. Instantaneous contact ellipse center bi = 0. The clearance bj (j ≠ i) at other discrete points along the major axis of the ellipse is given by (17) [12]. bM0 is the normal clearance between the two teeth contacts.Under the action of discrete loadP, the gear teeth are elastically deformed. If the driving pinion is fixed and the driven gear tooth moves along the normal direction under load, the displacement coordination equation is [15](18)Fkpk+wk=Z+dk,k=I,II.Among them,(19)pk=p1,p2,…,pi,…,pnT,dk=d1,d2,…,di,…,dnT,Zk=Z1,1,…,1,…,1T,where pj (j = 1, 2, …, n) is the normal load at the discrete point j of the long axis of instantaneous contact ellipse of tooth pair k. dj (j = 1, 2, …, n) is the deformed tooth surface clearance at the discrete point j of the instantaneous contact ellipsoid of tooth pair k. Z is the normal displacement of gear teeth. [F]k is the normal synthetic flexibility matrix of tooth pair k.


### 4.2. Force Balance Conditions

Discrete loadspj (j = 1, 2, …, n) are satisfied as follows:(20)∑j=1npjΙ+∑j=1npjΙΙ=P.


### 4.3. Nonembedding Conditions

(21)
If
p
j
k
>
0
,
then
d
j
k
=
0
,
if
p
j
k
=
0
,
then
d
j
k
>
0.where k = I, II.


### 4.4. Loaded Tooth Contact Analysis

The contact problem of loaded gear teeth was solved by mathematical programming:(22)f=min∑j=12n+1Xj,−Fp+Z+d+X=w,P=eTp+X2n+1,(23)S.t.pj≥0,dj≥0,Z≥0,Xj≥0,pj=0ordj=0,where Xj (j = 1, 2, …, 2n) is the artificial variable. [X] = [X1, X2, …, X2n]T. Each element of the n-dimensional column vector [e] is 1.Solving equations (22) and (23) give the normal displacement Z after gear teeth deformation and the discrete load [p] at the discrete points of the long axis of the instantaneous contact ellipse. At the same time, the tooth surface normal clearance [d] at instantaneous contact ellipse long axis discrete point is obtained after gear teeth deformation.The transmission error of gear pair under load can be obtained by converting the normal displacementZ of gear tooth deformation into angle value. From the discrete load [p] at discrete points along the long axis of the instantaneous contact ellipse, the distribution coefficients of the loads I and II at a certain contact position are given as follows:(24)Lk=∑j=1npjkP,k=I,II.IfLk is less than 1, the current contact position for more pairs of gear meshing.The synthetical time-varying meshing stiffness of the inner gearing teeth is shown in Figure8.Figure 8
The synthetical time-varying meshing stiffness of the inner gearing teeth.Through the comprehensive deformation amount on the line of action caused by the flexible inner ring gear, the deformation stiffness of the flexible inner ring gear is obtained as shown in Figure9. It can be seen from Figure 9 that the stiffness at the positions of the support points will increase significantly, which is consistent with the actual situation. At the same time, the synthetical time-varying meshing stiffness of inner gear in the meshing process is composed of two parts, namely, meshing stiffness generated by tooth deformation and deformation stiffness of flexible inner ring gear. After the normal meshing force of the tooth is decomposed (see Figure 10), the stiffness under different resolution is obtained. The synthetical meshing stiffness of inner gearing is shown in Figure 11.Figure 9
The meshing stiffness caused by the flexibility of the inner ring gear.Figure 10
Displacement of inner ring gear deformation along the line of action (including force decomposition).Figure 11
The synthetical meshing stiffness of inner gearing: (a) full circumference and (b) one-third.
(a)
(b)As shown in Figure11, the synthetical meshing stiffness of inner gearing is shown in Figure 11, where Figure 11(b) is the partial magnification of Figure 11(a). It can be seen from Figure 11 that the time-varying meshing stiffness of the gear teeth formed small fluctuations on the deformation stiffness of the flexible inner ring gear, and the overall comprehensive meshing stiffness was complex. The detailed analysis in this paper laid a very important foundation for the later study on the dynamics of the planetary transmission system. In this paper, five supporting points are used for the flexible inner ring gear (corresponding modifications can be made according to the actual supporting points). The selection of five supporting points here is to make it more convenient and obvious to see the overall impact of the flexibility of the inner ring gear on the meshing stiffness. By combining the geometrical structure of the inner ring gear, the whole inner ring gear is divided into five segments of the curved beam, and a comprehensive internal mesh stiffness model with wheel tooth deformation and ring gear deformation is established by combining the curved beam theory. It lays an important theoretical foundation for the analysis of the gear transmission process.


## 4.1. Deformation Coordination Equation

Suppose there are two pairs of gear tooth I and II meshing at the same time. The load tooth contact analysis model shown in Figure7 shows the cross section of the tooth flank along the long axis of the contact ellipse. i is the center of instantaneous contact ellipse on the tooth pair, j is the discrete point along the long axis on the tooth pair, and w is the initial pitch before contact on the tooth pair.Figure 7
The model of helical gear LTCA.Before gear deformation, the teeth of I and II tooth surface initial clearance are(13)wk=δk+bk,k=I,II,(14)wk=w1,w2,…,wi,…,wnT,(15)bk=b1,b2,…,bi,…,bnT,(16)δk=δ1,1,…,1,…,1T,(17)bM0=x1−x22+y1−y22+z1−z22,where n is the number of discrete points on the long axis of the instantaneous contact ellipse. bj (j = 1, 2, …, n) is the tooth surface normal clearance at the discrete point j of the long axis of the instantaneous contact ellipse. δ is the transmission error of gear pair k. Instantaneous contact ellipse center bi = 0. The clearance bj (j ≠ i) at other discrete points along the major axis of the ellipse is given by (17) [12]. bM0 is the normal clearance between the two teeth contacts.Under the action of discrete loadP, the gear teeth are elastically deformed. If the driving pinion is fixed and the driven gear tooth moves along the normal direction under load, the displacement coordination equation is [15](18)Fkpk+wk=Z+dk,k=I,II.Among them,(19)pk=p1,p2,…,pi,…,pnT,dk=d1,d2,…,di,…,dnT,Zk=Z1,1,…,1,…,1T,where pj (j = 1, 2, …, n) is the normal load at the discrete point j of the long axis of instantaneous contact ellipse of tooth pair k. dj (j = 1, 2, …, n) is the deformed tooth surface clearance at the discrete point j of the instantaneous contact ellipsoid of tooth pair k. Z is the normal displacement of gear teeth. [F]k is the normal synthetic flexibility matrix of tooth pair k.


## 4.2. Force Balance Conditions

Discrete loadspj (j = 1, 2, …, n) are satisfied as follows:(20)∑j=1npjΙ+∑j=1npjΙΙ=P.


## 4.3. Nonembedding Conditions

(21)
If
p
j
k
>
0
,
then
d
j
k
=
0
,
if
p
j
k
=
0
,
then
d
j
k
>
0.where k = I, II.


## 4.4. Loaded Tooth Contact Analysis

The contact problem of loaded gear teeth was solved by mathematical programming:(22)f=min∑j=12n+1Xj,−Fp+Z+d+X=w,P=eTp+X2n+1,(23)S.t.pj≥0,dj≥0,Z≥0,Xj≥0,pj=0ordj=0,where Xj (j = 1, 2, …, 2n) is the artificial variable. [X] = [X1, X2, …, X2n]T. Each element of the n-dimensional column vector [e] is 1.Solving equations (22) and (23) give the normal displacement Z after gear teeth deformation and the discrete load [p] at the discrete points of the long axis of the instantaneous contact ellipse. At the same time, the tooth surface normal clearance [d] at instantaneous contact ellipse long axis discrete point is obtained after gear teeth deformation.The transmission error of gear pair under load can be obtained by converting the normal displacementZ of gear tooth deformation into angle value. From the discrete load [p] at discrete points along the long axis of the instantaneous contact ellipse, the distribution coefficients of the loads I and II at a certain contact position are given as follows:(24)Lk=∑j=1npjkP,k=I,II.IfLk is less than 1, the current contact position for more pairs of gear meshing.The synthetical time-varying meshing stiffness of the inner gearing teeth is shown in Figure8.Figure 8
The synthetical time-varying meshing stiffness of the inner gearing teeth.Through the comprehensive deformation amount on the line of action caused by the flexible inner ring gear, the deformation stiffness of the flexible inner ring gear is obtained as shown in Figure9. It can be seen from Figure 9 that the stiffness at the positions of the support points will increase significantly, which is consistent with the actual situation. At the same time, the synthetical time-varying meshing stiffness of inner gear in the meshing process is composed of two parts, namely, meshing stiffness generated by tooth deformation and deformation stiffness of flexible inner ring gear. After the normal meshing force of the tooth is decomposed (see Figure 10), the stiffness under different resolution is obtained. The synthetical meshing stiffness of inner gearing is shown in Figure 11.Figure 9
The meshing stiffness caused by the flexibility of the inner ring gear.Figure 10
Displacement of inner ring gear deformation along the line of action (including force decomposition).Figure 11
The synthetical meshing stiffness of inner gearing: (a) full circumference and (b) one-third.
(a)
(b)As shown in Figure11, the synthetical meshing stiffness of inner gearing is shown in Figure 11, where Figure 11(b) is the partial magnification of Figure 11(a). It can be seen from Figure 11 that the time-varying meshing stiffness of the gear teeth formed small fluctuations on the deformation stiffness of the flexible inner ring gear, and the overall comprehensive meshing stiffness was complex. The detailed analysis in this paper laid a very important foundation for the later study on the dynamics of the planetary transmission system. In this paper, five supporting points are used for the flexible inner ring gear (corresponding modifications can be made according to the actual supporting points). The selection of five supporting points here is to make it more convenient and obvious to see the overall impact of the flexibility of the inner ring gear on the meshing stiffness. By combining the geometrical structure of the inner ring gear, the whole inner ring gear is divided into five segments of the curved beam, and a comprehensive internal mesh stiffness model with wheel tooth deformation and ring gear deformation is established by combining the curved beam theory. It lays an important theoretical foundation for the analysis of the gear transmission process.


## 5. Conclusion

By segmenting the inner ring gear into a curved beam, an algorithm and a model for calculating the meshing stiffness of the flexible inner ring gear are established. In the model, the effects of the parameters such as the supporting mode, supporting quantity, the thickness, and shape of the sections about the meshing stiffness of the planetary gear transmission system are considered comprehensively. At the same time, the comparison with the finite element model verifies the accuracy and reliability of the method. This study provides the basis and method for the optimization design of the flexible inner ring gear of planetary gear transmission, which is of great engineering significance. It also provides a more accurate model and foundation for studying the dynamic performance of the planetary transmission system.



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*Source: 2324546-2019-04-23.xml*