# Research on the Influence of Time-Varying Excitation on Vibration Characteristics of the Spiral Bevel Geared Transmission System with Broken Teeth

Authors: Dalian Yang; Liman Chen; Lingli Jiang; Ping Wang; Jie Tao
Journal: Shock and Vibration
 (2021)

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## Abstract

Due to heavy and alternating loads of working conditions, spiral bevel gears are prone to broken tooth failures. To solve the problem of vibration characteristic of spiral bevel geared transmission with broken tooth failures that is unknown, this study, considering time-varying mesh stiffness and friction excitation, proposed a torsional vibration dynamic model of spiral bevel geared transmission, which has more simple transmission path and the smaller signal attenuation. First, the time-varying excitations of various broken tooth failure are calculated and introduced into the torsional vibration dynamic model. The vibration response of spiral bevel geared transmission with various broken tooth failures is analysed in the time-frequency domain. Then, the sensitivity of the time-domain statistical index and the frequency domain components to different broken tooth failures are studied. Finally, the correctness of the simulation is verified by experiment. The results show that the crest factor is sensitive to minor tooth failure (10–30%), while kurtosis is sensitive to severe failure (30–60%). With the increase of degrees of broken tooth failure, the energy of the low-frequency band increases obviously.


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## Body

## 1. Introduction

Spiral bevel geared transmission system has been widely used in industrial machinery, automobile, and aviation due to its advantages of high speed, heavy load, and smooth operation. Spiral bevel gears often suffer from alternating loads in the working process and are prone to tooth failure [1–5]. The fracture of gear tooth will change the original time-varying excitation of the transmission system, which will aggravate the vibration of the transmission, reduce the transmission efficiency, and endanger the safety of equipment [6–9]. It is necessary to explore the relationship between the time-varying excitation and response characteristics of the spiral bevel geared transmission system for mechanical state evaluation and health maintenance.The spiral bevel geared transmission is a time-varying nonlinear system. To study the torsional vibration characteristics of the spiral bevel geared transmission system with broken tooth, the time-varying excitation of the transmission under the failure state should be defined first. Time-varying meshing stiffness, as a major time-varying excitation of the geared transmission system, has become the focus of domestic and foreign scholars [10–12]. For example, Chen et al. [13] simplified the gear tooth into a cantilever beam to study the analytical calculation model of time-varying meshing stiffness and obtain the static meshing stiffness. Wang [14, 15] calculated the analytic solutions of time-varying meshing stiffness of spur and helical gears using the slice method and explored the influences of factors such as misalignment, lead crown relief, and axial mesh force on time-varying meshing stiffness of gears. Tang and Pu [16] established the meshing model of spiral bevel gears by using finite element software and then obtained dynamic and more accurate time-varying mesh stiffness. In recent years, the research results found that another important time-varying excitation friction moment has caused the attention of scholars [17, 18]. So, it is proposed that both time-varying meshing stiffness and time-varying friction moment must be considered in the analysis of transmission [19]. The existing research work is mostly based on cylindrical geared transmission [20–22] and has few research studies on the spiral bevel geared transmission system. In order to study the vibration characteristics of gear transmission, scholars have given a variety of dynamic models [23]. Since the geared transmission mainly transmits torque, torsional vibration more directly reflects the operating state of the system compared with bending vibration, and the torsional vibration transmission path is simple, with less signal attenuation [24]. Therefore, the torsional vibration model is widely used in the fault dynamics analysis of the spiral bevel gear transmission system. For example, Zhang et al. [25] studied the mathematical model of the meshing process and typical gear failures and demonstrated the superiority of the torsional vibration analysis method in failure diagnosis of geared transmission. Yang et al. [26] considered time-varying meshing stiffness and time-varying friction to establish a failure model of spur gear with broken tooth and studied the torsional vibration characteristics of the transmission system. Doan and Karpat [27] established a dynamic model of the spur geared transmission containing the broken tooth failure and identified the broken tooth failure using torsional vibration response. To sum up, scholars have carried out extensive research studies on the vibration characteristics of geared transmission with failures, among which there are few studies about broken tooth failures with time-varying excitation. These research studies that are focused on torsional vibration response of spiral bevel geared transmission are rarely involved.Aiming at these problems, this study intends to propose a dynamic model of spiral bevel geared transmission that considering time-varying mesh stiffness and friction excitation calculates the time-varying excitation with broken tooth failure and then studies the torsional vibration response characteristics in time and frequency domain. In the end, the correctness of the simulation is verified by experiments, which can provide theoretical reference for the fault diagnosis of the spiral bevel geared transmission system.


## 2. Dynamic Model of the Spiral Bevel Geared Transmission System

### 2.1. Mathematical Model of the Spiral Bevel Geared Transmission System

The geared transmission system is a continuous model with infinite degrees of freedom. The finite element method is used to simplify the continuous model into a combination of finite elements connected to each other at the nodes, so that the problem becomes a mechanical problem with finite degrees of freedom. Thus, it can be solved by using linear equations. For torsional vibration, the discrete mechanical model of the spiral bevel geared transmission system includes mass element, elastic element, and damping element. The simplified dynamic model of the transmission system is shown in Figure1.Figure 1
Dynamic model of the spiral bevel geared transmission system.Ie and Ig are, respectively, the equivalent moment of inertia of pinion and gear. Suppose the system has n degrees of freedom, its generalized coordinates are θ1,θ2,…,θk,θk+1,…,θn−1,θn. The dynamic equation of the transmission system is established by using the finite element method as follows:(1)Iθ¨+Cθ˙+Kθ=Q,where I is the rotational inertia matrix, I=diagJ1J2J3⋯JkJk+1⋯Jn−1JnT, and J is the moment of inertia of each microelement. The moment of inertia of pinion and gear are Jk and Jk+1, respectively.C is the damping matrix:(2)C=c1−c1−c1c1+c2⋱−c2⋱⋱Ck−1+Cgtrg2−Cgtrgrp−CgtrgrpCk+2+Cgtrp2⋱⋱⋱cn−3+cn−2−cn−2−cn−2cn−1.Ci is the torsional damping of each element:(3)Ci=2ζki1/Ji+1/Ji+11/2.Cg is the meshing damping:(4)Cg=2ζmKgrg2/Jk+rp2/Jk+11/2,where rp and rg are the base radius of the main and driven gears, respectively, ζ is the damping ratio of the axial element, and ζm is the mesh damping ratio.K is the torsional stiffness matrix:(5)K=k1−k1−k1k1+k2⋱−k2⋱⋱kk−1+Kgtrg2−Kgtrgrp−Kgtrgrpkk+2+Kgtrp2⋱⋱⋱kn−3+kn−2−kn−2−kn−2kn−1,where ki is the torsional stiffness of axial element, and Kgt is the time-varying meshing stiffness.Q is the excitation matrix:(6)Q=Tin0⋯FPtrp+TfpFgtrg−Tfg⋯0−ToutT,where Fpt and Fgt are, respectively, the dynamic meshing forces of the pinion and gear, Tin and Tout are, respectively, the input and load torque, and Tfp and Tfg are the time-varying friction moments of the main and driven gears, respectively.


### 2.2. Mathematical Model of Time-Varying Meshing Stiffness

The contact ratio of gear is not an integer, and the number of the tooth involved in the mesh process changes periodically with time, so the meshing stiffness of the gear teeth also changes periodically with time, and the stiffness excitation makes the dynamic equation of the geared transmission contain time-varying coefficient, which makes it a time-varying nonlinear system. The general expression of time-varying mesh stiffness of single-teeth is shown in(7)kn=Fntunt,where Fnt is the normal dynamic meshing force acting on the tooth profile surface, and unt is the comprehensive elastic deformation of single pair gear tooth, which includes contact elastic deformation uh and the displacement of tooth contact caused by tooth bending ub, so unt can get by(8)un=∑i=12uhi+∑i=12ubi.When multitooth meshing occurs, the multipair tooth are coupled in parallel. Therefore, the time-varying mesh stiffness of the gears can be expressed as follows:(9)km=∑i=1pkni,where p is the number of gear pair in contact process.


### 2.3. Mathematical Model of Time-Varying Friction Torque of Spiral Bevel Gears

At present, the contact analysis theory of spiral bevel gears is not mature. To simplify the calculation, the spiral bevel gears are equivalent to helical gears in this study. The friction moment calculation model in literature [15] was adopted, which defined that gear has multiple contact lines. When the contact line is located outside the pitch circle, the friction force is positive, while the friction force inside the pitch circle is negative, and its direction is perpendicular to the contact line. In this study, the form of broken tooth perpendicular to the direction of tooth width is studied. Assuming that the contact line is uniformly distributed in the direction of tooth width, the contact area of broken tooth is shown in Figure 2, where Pt,Pn, and αb are the transverse pitch, normal pitch, and base helix angle, respectively.L′ is the length of the broken tooth along the width of equivalent gear, and L1,L2,L3 are the lengths of contact line at different states. Equation (10) is a friction calculation formula based on the dynamic engagement line. The friction on the ith contact line is as follows:(10)Ffi=−μFLΔLi,i=1,…,n,where F is the normal force acting on the tooth surface(N), L is the total length of the contact lines(mm), ΔLi is the difference between the length of two segments cutoff by the nodal circle of the contact line (mm), and μ is the coefficient of friction. Then, the total friction is calculated:(11)Ff=∑i=1nFfi,i=1,…,n.Figure 2
Diagram of meshing contact area of broken teeth.
(a)(b)The sign convention of the frictional torque is considered as positive when it facilitates the rotation and negative otherwise. The formula for calculating the friction torque on the contact line of theith line is as follows:(12)Tfi=∑inμFfiΔli,i=1,…,n,where Δli is the friction arm on the ith contact line.


## 2.1. Mathematical Model of the Spiral Bevel Geared Transmission System

The geared transmission system is a continuous model with infinite degrees of freedom. The finite element method is used to simplify the continuous model into a combination of finite elements connected to each other at the nodes, so that the problem becomes a mechanical problem with finite degrees of freedom. Thus, it can be solved by using linear equations. For torsional vibration, the discrete mechanical model of the spiral bevel geared transmission system includes mass element, elastic element, and damping element. The simplified dynamic model of the transmission system is shown in Figure1.Figure 1
Dynamic model of the spiral bevel geared transmission system.Ie and Ig are, respectively, the equivalent moment of inertia of pinion and gear. Suppose the system has n degrees of freedom, its generalized coordinates are θ1,θ2,…,θk,θk+1,…,θn−1,θn. The dynamic equation of the transmission system is established by using the finite element method as follows:(1)Iθ¨+Cθ˙+Kθ=Q,where I is the rotational inertia matrix, I=diagJ1J2J3⋯JkJk+1⋯Jn−1JnT, and J is the moment of inertia of each microelement. The moment of inertia of pinion and gear are Jk and Jk+1, respectively.C is the damping matrix:(2)C=c1−c1−c1c1+c2⋱−c2⋱⋱Ck−1+Cgtrg2−Cgtrgrp−CgtrgrpCk+2+Cgtrp2⋱⋱⋱cn−3+cn−2−cn−2−cn−2cn−1.Ci is the torsional damping of each element:(3)Ci=2ζki1/Ji+1/Ji+11/2.Cg is the meshing damping:(4)Cg=2ζmKgrg2/Jk+rp2/Jk+11/2,where rp and rg are the base radius of the main and driven gears, respectively, ζ is the damping ratio of the axial element, and ζm is the mesh damping ratio.K is the torsional stiffness matrix:(5)K=k1−k1−k1k1+k2⋱−k2⋱⋱kk−1+Kgtrg2−Kgtrgrp−Kgtrgrpkk+2+Kgtrp2⋱⋱⋱kn−3+kn−2−kn−2−kn−2kn−1,where ki is the torsional stiffness of axial element, and Kgt is the time-varying meshing stiffness.Q is the excitation matrix:(6)Q=Tin0⋯FPtrp+TfpFgtrg−Tfg⋯0−ToutT,where Fpt and Fgt are, respectively, the dynamic meshing forces of the pinion and gear, Tin and Tout are, respectively, the input and load torque, and Tfp and Tfg are the time-varying friction moments of the main and driven gears, respectively.


## 2.2. Mathematical Model of Time-Varying Meshing Stiffness

The contact ratio of gear is not an integer, and the number of the tooth involved in the mesh process changes periodically with time, so the meshing stiffness of the gear teeth also changes periodically with time, and the stiffness excitation makes the dynamic equation of the geared transmission contain time-varying coefficient, which makes it a time-varying nonlinear system. The general expression of time-varying mesh stiffness of single-teeth is shown in(7)kn=Fntunt,where Fnt is the normal dynamic meshing force acting on the tooth profile surface, and unt is the comprehensive elastic deformation of single pair gear tooth, which includes contact elastic deformation uh and the displacement of tooth contact caused by tooth bending ub, so unt can get by(8)un=∑i=12uhi+∑i=12ubi.When multitooth meshing occurs, the multipair tooth are coupled in parallel. Therefore, the time-varying mesh stiffness of the gears can be expressed as follows:(9)km=∑i=1pkni,where p is the number of gear pair in contact process.


## 2.3. Mathematical Model of Time-Varying Friction Torque of Spiral Bevel Gears

At present, the contact analysis theory of spiral bevel gears is not mature. To simplify the calculation, the spiral bevel gears are equivalent to helical gears in this study. The friction moment calculation model in literature [15] was adopted, which defined that gear has multiple contact lines. When the contact line is located outside the pitch circle, the friction force is positive, while the friction force inside the pitch circle is negative, and its direction is perpendicular to the contact line. In this study, the form of broken tooth perpendicular to the direction of tooth width is studied. Assuming that the contact line is uniformly distributed in the direction of tooth width, the contact area of broken tooth is shown in Figure 2, where Pt,Pn, and αb are the transverse pitch, normal pitch, and base helix angle, respectively.L′ is the length of the broken tooth along the width of equivalent gear, and L1,L2,L3 are the lengths of contact line at different states. Equation (10) is a friction calculation formula based on the dynamic engagement line. The friction on the ith contact line is as follows:(10)Ffi=−μFLΔLi,i=1,…,n,where F is the normal force acting on the tooth surface(N), L is the total length of the contact lines(mm), ΔLi is the difference between the length of two segments cutoff by the nodal circle of the contact line (mm), and μ is the coefficient of friction. Then, the total friction is calculated:(11)Ff=∑i=1nFfi,i=1,…,n.Figure 2
Diagram of meshing contact area of broken teeth.
(a)(b)The sign convention of the frictional torque is considered as positive when it facilitates the rotation and negative otherwise. The formula for calculating the friction torque on the contact line of theith line is as follows:(12)Tfi=∑inμFfiΔli,i=1,…,n,where Δli is the friction arm on the ith contact line.


## 3. Analysis of Torsional Vibration Characteristics of the Spiral Bevel Geared Transmission System with Broken Tooth

### 3.1. Finite Element Model of Spiral Bevel Gear Pair

Spiral bevel gears pair is compact in structure, stable in transmission, and able to change the direction of power transmission. In this study, a spiral bevel geared transmission is taken as an example to study the dynamic response of the transmission with time-varying excitation. Its structure is shown in Figure3, and its structural parameters are shown in Table 1.Figure 3
Diagram of spiral bevel gear pair.Table 1
Design parameters of gears.
ParameterPinionGearModulus7.987.98Number of teeth1441Pressure angle (°)2020Helix angle (°)3535Angle of shafts (°)9090Base width (mm)5555Mass (kg)1.5112.955Moment of inertia (kg∗ m2)9.25×10−46.8×10−23D modelling software (UG) was used to establish the solid model of spiral bevel gear pair with broken teeth, which was imported into ANSYS for analysis. Contact area of tooth pair use CONTA174 unit and TARGET170 unit, the solid model adopt the SOLID186 unit, the broken area use the tetrahedrons dividing method, and the normal region use the hex-dominant division method. In order to save computing resources, spiral bevel gears were cut and 5 pairs of gear tooth were reserved for dynamic meshing analysis. The meshing simulation model of spiral bevel gears is shown in Figure4. The ratio of the arc length of the gear tooth to the length of the broken tooth represents the different degrees of the broken tooth failure, namely, L−/S×100%=20%,30%,40%,50%,60%, and the geometric model of broken teeth is shown in Figure 5.Figure 4
Meshing simulation model of spiral bevel gear.Figure 5
Geometric model of broken teeth.


### 3.2. Time-Varying Excitation Analysis of Spiral Bevel Gears with Broken Tooth

#### 3.2.1. Time-Varying Mesh Stiffness Analysis

The broken tooth failure will lead to reduction of time-varying meshing stiffness. The more serious the broken tooth failure is, the more meshing stiffness of a single-teeth decreases, as shown in Figure6(a). Time-varying meshing stiffness of multiple teeth is calculated according to the contact ratio and the loading contact analysis, as shown in Figure 6(b).Figure 6
Time-varying meshing stiffness of spiral bevel gears with broken teeth: (a) tvms of single-teeth and (b) tvms of multitooth.
(a)(b)


#### 3.2.2. Time-Varying Friction Moment Analysis

The time-varying friction torque under broken tooth failure is shown in Figure7. It can be seen from Figure 7 that the value of the friction torque has a sudden change at the pitch circle. This is because the direction of the tooth surface friction will change to the opposite direction after crossing the pitch circle, which conforms to the existing gear meshing principle. At the same time, as the degree of broken tooth increases, the value of time-varying friction torque decreases to varying degrees. Because spiral bevel gears belong to multitooth meshing, a single-tooth breaks down and causes a limited reduction in friction torque.Figure 7
Time-varying friction torque with broken tooth.


### 3.3. Torsional Vibration Characteristics Analysis of the Transmission System with Broken Tooth

Angular displacement calculation is the basic content of torsional vibration research. In this study, the numerical method is used to solve equation (1). This numerical method does not need to distinguish whether the system contains proportional damping and has good stability. Generally, when θ>1.37, the algorithm can be guaranteed to be unconditionally stable. In this study, θ=1.4, and the input speed is 1000 r/min.


#### 3.3.1. Time-Domain Response Characteristics of the Transmission System

Torsional vibration essentially reflects the relative value of angular displacement between two points along the axis, so formula (13) is used to measure torsional vibration of the spiral bevel geared transmission system.(13)xt=Rb2θ2−Rb1θ1,where θ1,θ2 represent the angular displacements at the pinion and gear, respectively. Rb1,Rb2 represent the base circle radius of pinion and gear, respectively.It can be seen from Figure8, when the spiral bevel gear has broken tooth failure, the torsional vibration response of the system has obvious periodic impact vibration. After the friction force is included in the model, the vibration amplitude increases to some extent, and the more serious the broken tooth failure is, the more the vibration amplitude increases.Figure 8
Time-domain response of torsional vibration of the transmission system. (a) Normal teeth. (b) 20%. (c) 30%. (d) 40%.
(a)(b)(c)(d)For further analysis, the influence of different degrees of broken tooth failure on torsional vibration, three statistical indexes, such as root mean square error (RMS), kurtosis, and crest factor is used to analyse the time-domain response. The statistics index of time-domain response of torsional vibration with various degrees of broken teeth failures is shown in Figure9. The crest factor increases significantly before the broken tooth failure reaches 30%, that is, the crest factor is more sensitive to the minor broken tooth failure, while during 30–60% of the broken tooth failure, the change is tiny, that is, the crest factor is not sensitive to the serious broken tooth failure. Before the tooth failure reaches 30%, kurtosis has a small change, 30–40% has an increase, and 40–60% has an obvious increase. Kurtosis is not sensitive to minor tooth failure, but extremely sensitive to severe tooth failure.Figure 9
Time-domain statistical index.


#### 3.3.2. Frequency-Domain Response Characteristics of the Transmission System

As the increase of degrees of broken tooth failures, the response characteristics of torsional vibration of the system in frequency domain are shown in Figure10. It can be clearly seen from Figure 10 that there is obvious meshing frequency (fe=233Hz) and its harmonic frequency. After the gear tooth failure occurs, the rotation frequency (fr=16.6Hz) and the side frequency band of mesh frequency appear in the spectrum diagram. With the aggravation of failure degree, the side bands of meshing frequency have enriched, especially the low-frequency bands before the first-order meshing frequency. As the single-tooth failure is studied in this study, the first-order rotation frequency (16.6Hz) is distinct, and the multifold rotation frequency appears in the spectrum diagram.Figure 10
The spectrum diagram of the broken tooth failure. (a) Normal teeth. (b) 20%. (c) 30%. (d) 40%. (e) 50%. (f) 60%.
(a)(b)(c)(d)(e)(f)


## 3.1. Finite Element Model of Spiral Bevel Gear Pair

Spiral bevel gears pair is compact in structure, stable in transmission, and able to change the direction of power transmission. In this study, a spiral bevel geared transmission is taken as an example to study the dynamic response of the transmission with time-varying excitation. Its structure is shown in Figure3, and its structural parameters are shown in Table 1.Figure 3
Diagram of spiral bevel gear pair.Table 1
Design parameters of gears.
ParameterPinionGearModulus7.987.98Number of teeth1441Pressure angle (°)2020Helix angle (°)3535Angle of shafts (°)9090Base width (mm)5555Mass (kg)1.5112.955Moment of inertia (kg∗ m2)9.25×10−46.8×10−23D modelling software (UG) was used to establish the solid model of spiral bevel gear pair with broken teeth, which was imported into ANSYS for analysis. Contact area of tooth pair use CONTA174 unit and TARGET170 unit, the solid model adopt the SOLID186 unit, the broken area use the tetrahedrons dividing method, and the normal region use the hex-dominant division method. In order to save computing resources, spiral bevel gears were cut and 5 pairs of gear tooth were reserved for dynamic meshing analysis. The meshing simulation model of spiral bevel gears is shown in Figure4. The ratio of the arc length of the gear tooth to the length of the broken tooth represents the different degrees of the broken tooth failure, namely, L−/S×100%=20%,30%,40%,50%,60%, and the geometric model of broken teeth is shown in Figure 5.Figure 4
Meshing simulation model of spiral bevel gear.Figure 5
Geometric model of broken teeth.


## 3.2. Time-Varying Excitation Analysis of Spiral Bevel Gears with Broken Tooth

### 3.2.1. Time-Varying Mesh Stiffness Analysis

The broken tooth failure will lead to reduction of time-varying meshing stiffness. The more serious the broken tooth failure is, the more meshing stiffness of a single-teeth decreases, as shown in Figure6(a). Time-varying meshing stiffness of multiple teeth is calculated according to the contact ratio and the loading contact analysis, as shown in Figure 6(b).Figure 6
Time-varying meshing stiffness of spiral bevel gears with broken teeth: (a) tvms of single-teeth and (b) tvms of multitooth.
(a)(b)


### 3.2.2. Time-Varying Friction Moment Analysis

The time-varying friction torque under broken tooth failure is shown in Figure7. It can be seen from Figure 7 that the value of the friction torque has a sudden change at the pitch circle. This is because the direction of the tooth surface friction will change to the opposite direction after crossing the pitch circle, which conforms to the existing gear meshing principle. At the same time, as the degree of broken tooth increases, the value of time-varying friction torque decreases to varying degrees. Because spiral bevel gears belong to multitooth meshing, a single-tooth breaks down and causes a limited reduction in friction torque.Figure 7
Time-varying friction torque with broken tooth.


## 3.2.1. Time-Varying Mesh Stiffness Analysis

The broken tooth failure will lead to reduction of time-varying meshing stiffness. The more serious the broken tooth failure is, the more meshing stiffness of a single-teeth decreases, as shown in Figure6(a). Time-varying meshing stiffness of multiple teeth is calculated according to the contact ratio and the loading contact analysis, as shown in Figure 6(b).Figure 6
Time-varying meshing stiffness of spiral bevel gears with broken teeth: (a) tvms of single-teeth and (b) tvms of multitooth.
(a)(b)


## 3.2.2. Time-Varying Friction Moment Analysis

The time-varying friction torque under broken tooth failure is shown in Figure7. It can be seen from Figure 7 that the value of the friction torque has a sudden change at the pitch circle. This is because the direction of the tooth surface friction will change to the opposite direction after crossing the pitch circle, which conforms to the existing gear meshing principle. At the same time, as the degree of broken tooth increases, the value of time-varying friction torque decreases to varying degrees. Because spiral bevel gears belong to multitooth meshing, a single-tooth breaks down and causes a limited reduction in friction torque.Figure 7
Time-varying friction torque with broken tooth.


## 3.3. Torsional Vibration Characteristics Analysis of the Transmission System with Broken Tooth

Angular displacement calculation is the basic content of torsional vibration research. In this study, the numerical method is used to solve equation (1). This numerical method does not need to distinguish whether the system contains proportional damping and has good stability. Generally, when θ>1.37, the algorithm can be guaranteed to be unconditionally stable. In this study, θ=1.4, and the input speed is 1000 r/min.


### 3.3.1. Time-Domain Response Characteristics of the Transmission System

Torsional vibration essentially reflects the relative value of angular displacement between two points along the axis, so formula (13) is used to measure torsional vibration of the spiral bevel geared transmission system.(13)xt=Rb2θ2−Rb1θ1,where θ1,θ2 represent the angular displacements at the pinion and gear, respectively. Rb1,Rb2 represent the base circle radius of pinion and gear, respectively.It can be seen from Figure8, when the spiral bevel gear has broken tooth failure, the torsional vibration response of the system has obvious periodic impact vibration. After the friction force is included in the model, the vibration amplitude increases to some extent, and the more serious the broken tooth failure is, the more the vibration amplitude increases.Figure 8
Time-domain response of torsional vibration of the transmission system. (a) Normal teeth. (b) 20%. (c) 30%. (d) 40%.
(a)(b)(c)(d)For further analysis, the influence of different degrees of broken tooth failure on torsional vibration, three statistical indexes, such as root mean square error (RMS), kurtosis, and crest factor is used to analyse the time-domain response. The statistics index of time-domain response of torsional vibration with various degrees of broken teeth failures is shown in Figure9. The crest factor increases significantly before the broken tooth failure reaches 30%, that is, the crest factor is more sensitive to the minor broken tooth failure, while during 30–60% of the broken tooth failure, the change is tiny, that is, the crest factor is not sensitive to the serious broken tooth failure. Before the tooth failure reaches 30%, kurtosis has a small change, 30–40% has an increase, and 40–60% has an obvious increase. Kurtosis is not sensitive to minor tooth failure, but extremely sensitive to severe tooth failure.Figure 9
Time-domain statistical index.


### 3.3.2. Frequency-Domain Response Characteristics of the Transmission System

As the increase of degrees of broken tooth failures, the response characteristics of torsional vibration of the system in frequency domain are shown in Figure10. It can be clearly seen from Figure 10 that there is obvious meshing frequency (fe=233Hz) and its harmonic frequency. After the gear tooth failure occurs, the rotation frequency (fr=16.6Hz) and the side frequency band of mesh frequency appear in the spectrum diagram. With the aggravation of failure degree, the side bands of meshing frequency have enriched, especially the low-frequency bands before the first-order meshing frequency. As the single-tooth failure is studied in this study, the first-order rotation frequency (16.6Hz) is distinct, and the multifold rotation frequency appears in the spectrum diagram.Figure 10
The spectrum diagram of the broken tooth failure. (a) Normal teeth. (b) 20%. (c) 30%. (d) 40%. (e) 50%. (f) 60%.
(a)(b)(c)(d)(e)(f)


## 3.3.1. Time-Domain Response Characteristics of the Transmission System

Torsional vibration essentially reflects the relative value of angular displacement between two points along the axis, so formula (13) is used to measure torsional vibration of the spiral bevel geared transmission system.(13)xt=Rb2θ2−Rb1θ1,where θ1,θ2 represent the angular displacements at the pinion and gear, respectively. Rb1,Rb2 represent the base circle radius of pinion and gear, respectively.It can be seen from Figure8, when the spiral bevel gear has broken tooth failure, the torsional vibration response of the system has obvious periodic impact vibration. After the friction force is included in the model, the vibration amplitude increases to some extent, and the more serious the broken tooth failure is, the more the vibration amplitude increases.Figure 8
Time-domain response of torsional vibration of the transmission system. (a) Normal teeth. (b) 20%. (c) 30%. (d) 40%.
(a)(b)(c)(d)For further analysis, the influence of different degrees of broken tooth failure on torsional vibration, three statistical indexes, such as root mean square error (RMS), kurtosis, and crest factor is used to analyse the time-domain response. The statistics index of time-domain response of torsional vibration with various degrees of broken teeth failures is shown in Figure9. The crest factor increases significantly before the broken tooth failure reaches 30%, that is, the crest factor is more sensitive to the minor broken tooth failure, while during 30–60% of the broken tooth failure, the change is tiny, that is, the crest factor is not sensitive to the serious broken tooth failure. Before the tooth failure reaches 30%, kurtosis has a small change, 30–40% has an increase, and 40–60% has an obvious increase. Kurtosis is not sensitive to minor tooth failure, but extremely sensitive to severe tooth failure.Figure 9
Time-domain statistical index.


## 3.3.2. Frequency-Domain Response Characteristics of the Transmission System

As the increase of degrees of broken tooth failures, the response characteristics of torsional vibration of the system in frequency domain are shown in Figure10. It can be clearly seen from Figure 10 that there is obvious meshing frequency (fe=233Hz) and its harmonic frequency. After the gear tooth failure occurs, the rotation frequency (fr=16.6Hz) and the side frequency band of mesh frequency appear in the spectrum diagram. With the aggravation of failure degree, the side bands of meshing frequency have enriched, especially the low-frequency bands before the first-order meshing frequency. As the single-tooth failure is studied in this study, the first-order rotation frequency (16.6Hz) is distinct, and the multifold rotation frequency appears in the spectrum diagram.Figure 10
The spectrum diagram of the broken tooth failure. (a) Normal teeth. (b) 20%. (c) 30%. (d) 40%. (e) 50%. (f) 60%.
(a)(b)(c)(d)(e)(f)


## 4. Experimental Verification

### 4.1. Vibration Test of the Spiral Bevel Geared Transmission System with Broken Teeth

In order to verify the correctness of the simulation results, the vibration experiment of the spiral bevel geared transmission system with broken tooth failure was carried out. The spiral bevel gearbox used for the vibration test is shown in Figure11. The test equipment is composed of a governor, a motor, couplings, a pair of spiral bevel gears, and a load. The driving gear is used as the test gear to simulate three typical failure gears, namely, normal tooth, 1/3 broken tooth, and 2/3 broken tooth. Vibration signals were collected using B&K’s PULSE data acquisition system. During the test, the speed of the motor was kept constant at 1000 r/min by adjusting the governor, and the sampling frequency was 6.4 kHz.Figure 11
Spiral bevel gearbox test equipment.


### 4.2. Frequency Domain Response Analysis of Experimental Result

As can be seen from Figure12, when there are different degrees of broken teeth faults, the system response has obvious meshing frequency. When the system is a normal gear, the amplitude of low-frequency band is small, and the rotating frequency and its component is not obvious, as shown in Figure 12(a). When the system has a broken tooth failure (30%), the amplitude of the rotating frequency component caused by the broken tooth failure increases significantly, which also has an obvious fr, as shown in Figure 12(b).Figure 12
Test frequency domain response diagram of broken tooth failure.
(a)(b)


### 4.3. Analysis of the Influence of Time-Varying Friction Excitation on Low-Frequency Band

It can be seen from Figures10 and 12 that the more serious the broken tooth failure is, the more abundant the low-frequency band is, and the more energy it contains. Therefore, the energy of low-frequency band can be used to further study the influence of time-varying friction excitation on the dynamic response of the geared transmission system. The energy ratio is defined to represent the contribution of time-varying frictional excitation to low-frequency band energy, as shown in(14)ηlfb=Efb−Eb/Efb×100%,where Efb is the sum value of energy of the low-frequency band with the frictional excitation, and Eb is the sum value of energy of low-frequency band without frictional excitation.The variation of the contribution of experiment and simulation with different failure degrees of broken tooth is shown in Figure13. It can be seen from Figure 13 that the contribution of friction excitation to low-frequency band is 12% with no broken tooth failure. After broken tooth failure occurs, the friction excitation decreases, resulting in the decrease of the contribution to low-frequency band as the increase of failure degrees. The variation trend of the experiment and the simulation results are basically consistent, but the time-varying frictional excitation in the experiment has a greater contribution to the low-frequency band than the simulation results. The contribution is about 21% and 6% with normal tooth and 60% broken teeth failures, respectively. The difference may be caused by unbalanced excitation and mesh error excitation generated by tooth failures, both of which can provide energy for the low-frequency band.Figure 13
Influence of time-varying friction excitation on low-frequency band.


## 4.1. Vibration Test of the Spiral Bevel Geared Transmission System with Broken Teeth

In order to verify the correctness of the simulation results, the vibration experiment of the spiral bevel geared transmission system with broken tooth failure was carried out. The spiral bevel gearbox used for the vibration test is shown in Figure11. The test equipment is composed of a governor, a motor, couplings, a pair of spiral bevel gears, and a load. The driving gear is used as the test gear to simulate three typical failure gears, namely, normal tooth, 1/3 broken tooth, and 2/3 broken tooth. Vibration signals were collected using B&K’s PULSE data acquisition system. During the test, the speed of the motor was kept constant at 1000 r/min by adjusting the governor, and the sampling frequency was 6.4 kHz.Figure 11
Spiral bevel gearbox test equipment.


## 4.2. Frequency Domain Response Analysis of Experimental Result

As can be seen from Figure12, when there are different degrees of broken teeth faults, the system response has obvious meshing frequency. When the system is a normal gear, the amplitude of low-frequency band is small, and the rotating frequency and its component is not obvious, as shown in Figure 12(a). When the system has a broken tooth failure (30%), the amplitude of the rotating frequency component caused by the broken tooth failure increases significantly, which also has an obvious fr, as shown in Figure 12(b).Figure 12
Test frequency domain response diagram of broken tooth failure.
(a)(b)


## 4.3. Analysis of the Influence of Time-Varying Friction Excitation on Low-Frequency Band

It can be seen from Figures10 and 12 that the more serious the broken tooth failure is, the more abundant the low-frequency band is, and the more energy it contains. Therefore, the energy of low-frequency band can be used to further study the influence of time-varying friction excitation on the dynamic response of the geared transmission system. The energy ratio is defined to represent the contribution of time-varying frictional excitation to low-frequency band energy, as shown in(14)ηlfb=Efb−Eb/Efb×100%,where Efb is the sum value of energy of the low-frequency band with the frictional excitation, and Eb is the sum value of energy of low-frequency band without frictional excitation.The variation of the contribution of experiment and simulation with different failure degrees of broken tooth is shown in Figure13. It can be seen from Figure 13 that the contribution of friction excitation to low-frequency band is 12% with no broken tooth failure. After broken tooth failure occurs, the friction excitation decreases, resulting in the decrease of the contribution to low-frequency band as the increase of failure degrees. The variation trend of the experiment and the simulation results are basically consistent, but the time-varying frictional excitation in the experiment has a greater contribution to the low-frequency band than the simulation results. The contribution is about 21% and 6% with normal tooth and 60% broken teeth failures, respectively. The difference may be caused by unbalanced excitation and mesh error excitation generated by tooth failures, both of which can provide energy for the low-frequency band.Figure 13
Influence of time-varying friction excitation on low-frequency band.


## 5. Conclusion

In this study, the torsional vibration characteristics of the spiral bevel geared transmission system with various degrees of broken tooth failures are studied by considering the time-varying excitation. The following conclusions are drawn:(1)
The sensitivity of three time-domain statistical indexes, RMS, kurtosis, and crest factor to broken teeth failures were compared. It was found that the crest factor was sensitive to minor broken teeth failures (10%–30%), while kurtosis is sensitive to severe failure (30%–60%);(2)
As the degrees of broken tooth failures increase, the energy of low-frequency band increases obviously. Frictional excitation of normal teeth contributes approximately 12%–21% of the energy to the low-frequency band by a further study on the low-frequency band. And with the increase of the failure degrees, the value decreases from 17% to 5%.



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*Source: 8880851-2021-02-11.xml*