# Research on Multiple-Split Load Sharing Characteristics of 2-Stage External Meshing Star Gear System in Consideration of Displacement Compatibility

Authors: Shuai Mo; Shuai Ma; Guoguang Jin; Yidu Zhang; Chao Lv; Haruo Houjoh
Journal: Mathematical Problems in Engineering
 (2017)

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## Abstract

This paper studies the multiple-split load sharing mechanism of gears in two-stage external meshing planetary transmission system of aeroengine. According to the eccentric error, gear tooth thickness error, pitch error, installation error, and bearing manufacturing error, we performed the meshing error analysis of equivalent angles, respectively, and we also considered the floating meshing error caused by the variation of the meshing backlash, which is from the floating of all gears at the same time. Finally, we obtained the comprehensive angle meshing error of the two-stage meshing line, established a refined mathematical computational model of 2-stage external 3-split loading sharing coefficient in consideration of displacement compatibility, got the regular curves of the load sharing coefficient and load sharing characteristic curve of full floating multiple-split and multiple-stage system, and took the variation law of the floating track and the floating quantity of the center wheel. These provide a scientific theory to determine the load sharing coefficient, reasonable load distribution, and control tolerances in aviation design and manufacturing.


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## Body

## 1. Preface

Two-stage external meshing planetary transmission system is widely used in aviation and special precision transmission field. The T53-L-11 turbo-axis aircraft engine produced by Lycoming (US Company) used two-stage external meshing planetary transmission system as its reducer. Located in the engine head and installed in the intake box, reducer transports the motivation from free turbine shaft to the second sun gear after decreasing speed and increasing torque. Two-stage star gear transmission has multiple duplicate gears with fixed-axes to share the load, its star gears do not revolve, and its characteristics are power split, high transmission power, and only one-side load bearing, and so on. Two-stage star gear transmission uses two-stage star gears, without the ring gear, directly output by two external gears, so that it overcomes the alternating load of planet gear in traditional planetary gear transmission, the difficulty in processing of ring gear, the centrifugal force caused by the rotation of carrier, and intermittent lubrication of planet gear. The system strength, stiffness, and working life and reliability of transmission system have greatly improved by using two-stage fixed-axis external meshing gears. In this paper, a precise load sharing characteristic analysis model is established for all gears with angular displacement compatibility, including bearing manufacturing errors, gear manufacturing errors (eccentricity error, tooth thickness error, and pitch error), installation error, and the meshing error caused by the variation of the meshing backlash resulting from simultaneous floating of all the gears. Research results can be used for aircraft engine and other precision special transmission systems in load sharing coefficients determination, vibration noise reduction, structure optimization, and error precision control. This paper provides scientific theory for the gear machining and assembly process and reveals load sharing mechanism for the multiple-split system.The load sharing has great influence on vibration and noise of power split transmission systems; therefore, domestic and foreign scholars continue to explore and research the load sharing of power split systems. Kahraman et al. studied statics load sharing characteristic of the planetary transmission systems [1–4]; Singh established analysis model of the load sharing characteristic of the planetary transmission systems [5, 6]; Wink and Sepra studied the method of tooth surface load distribution [7]; Bao et al. studied the static load sharing characteristics of star gear and closed differential transmission systems [8, 9]; Du et al. studied the load sharing characteristics of the planetary transmission systems and dual power splitting systems [10, 11]; and Mo et al. researched the natural characteristics of double-helical star gearing system for GTF aeroengine and load sharing behavior of wind turbine gearbox [12–15]; Mantriota deals with the performance of power split transmissions in wind energy systems to identify the power split configurations that require the minimum rated power of the regulator system, to reduce costs and the power losses [16]. Zhu et al. established a dynamic analysis model for 2-stage star gear train, where in the transmission error and the time-varying stiffness and backlash the nonlinear differential equations with multiple backlashes were considered and solved [17]. Gu et al. proposed a new type of spiral bevel gears power split system with cross axes transmission and its structure and working state were explained based on different forms of gear power split transmission including parallel axes, star gear train, and planetary gear train [18]. Shigley and Mischke have done much research work on mechanical design [19].


## 2. Two-Stage External Meshing Star Gear Transmission System

A movement diagram of two-stage external meshing star gearing transmission system used in a certain type of aircraft engine was shown in Figure1. In each stage, 3 star gears and 2 external meshing were used, sun gear S1 in the first stage is input side, and sun gear S2 in the second stage is output side. Related parameters are shown in Table 1.Table 1
Star reducer gear parameters.
Name
Teeth number
Modulus
Input power
Input speed
Z
s
1
15
1.5 mm
100 kW
40000 r/min
Z
p
1
i
54
1.5 mm
Z
p
2
i
15
1.5 mm
Z
s
2
54
1.5 mmFigure 1
Two-stage external meshing planetary reducer movement diagram.


## 3. Load Sharing Mechanism of Two-Stage Star Gearing Transmission System

In planetary gear transmission, the center gear is usually used as a floating component. When the star gears are loaded unevenly, the floating component is forced to move until the load of several star gears tends to be evenly distributed. The load distribution diagrams of the sun gear in first stage and second stage are shown in Figure2. In ideal stiffness and manufacturing accuracy, sun gear S1 of first stage will float and the principal vector of Fs1p1i is 0: namely, Fs1p11+⋯+Fs1p13=0. And the main torque of sun gear S1 is equal to the input torque. Sun gear S2 of second stage will float, the principal vector of Fs2p2i is 0, namely, Fp21s2+⋯+Fp23s2=0, and the main torque of sun gear s2 is equal to the output torque.Figure 2
Load distribution between star gears.If the floating components are under uniform load, the three normal meshing forces constitute a closed equilateral triangle, so that the load of star gear tends to be uniform, to achieve the purpose of share loading, as shown in situations (a) and (c). If the amounts of floating component and structure design are unreasonable and the manufacturing and installation error become large enough, then the three normal meshing forces constitute equilateral triangle, load distribution of star gear is uneven, and load sharing effect is bad, as shown in situations (b) and (d). The force in the actual product is approximately equilateral triangle, which bring in the load sharing coefficient of transmission system.


## 4. Angular Meshing Error Analysis

### 4.1. Equivalent Angular Meshing Error on Meshing Line

Taking the most common influence of star gear system on load sharing as an example, the equivalent error of meshing error is analyzed along meshing line. Other related errors (such as axial skew error, position error of star gear hole, and runout error) are also available by similar process. Finally, the comprehensive angle meshing error is obtained.Manufacturing error and installation error of each component are shown in Figure3, o is the theoretical center position, o1 is the actual center position, and the distance between two points is the error; E is the manufacturing error, A is the installation error, β is the manufacturing error direction, γ is the installation error direction, ωs1 is the angular velocity of the sun gear 1, ωp1 is the angular velocity of the large star gear, ωp2 is the angular velocity of the small star gear, ωs2 is the angular velocity of the sun gear 2, αw1 is the meshing angle of the 1st external meshing, αw2 is the meshing angle of the 2st external meshing, ɸi is the position angle of the i star gear relative to the first star gear, ɸi=2πi-1/n, n is the number of star gears, t is the time, and subscripts s1/p1i/p2i/s2, respectively, represent the sun gear 1, the first-stage star gear i, the second-stage star gear i, and the sun gear 2. The equivalent error of meshing error is analyzed along the two-stage external meshing line. Supposing that the center of the star gear 1 is on the x-axis, as shown in Figure 4, the direction of the equivalent meshing error out of the meshing line is defined as positive.Figure 3
Diagram of manufacturing error and assemble error.Figure 4
Calculation model of load sharing coefficient.


### 4.2. Comprehensive Angular Meshing Error

The accumulated meshing errors on the meshing lines of individual component can be obtained by superimposing meshing errors.(1)φs1p1i=φEs1i+φAs1i+φEbs1i+φEs1p1i+φAs1pi+φEbs1p1i+φbps1+φbpp1i+φts1+φtp1iφp2is2=φEs2i+φAs2i+φEbs2i+φEp2is2+φAp2is2+φEbp2is2+φbps2+φbpp2i+φts2+φtp2i.The comprehensive meshing error between theith star gear and the 1st-stage sun gear is Δφs1p1i0Ts1p1i, and the meshing error between the 2nd-stage sun gear and the ith star gear is Δφp2is20Tpis2.(2)Δφs1p1i0Ts1p2i=φs1i+φs1p1i+φp1iΔφp2is20Tp2is2=φs2i+φp2is2+φp2i.


## 4.1. Equivalent Angular Meshing Error on Meshing Line

Taking the most common influence of star gear system on load sharing as an example, the equivalent error of meshing error is analyzed along meshing line. Other related errors (such as axial skew error, position error of star gear hole, and runout error) are also available by similar process. Finally, the comprehensive angle meshing error is obtained.Manufacturing error and installation error of each component are shown in Figure3, o is the theoretical center position, o1 is the actual center position, and the distance between two points is the error; E is the manufacturing error, A is the installation error, β is the manufacturing error direction, γ is the installation error direction, ωs1 is the angular velocity of the sun gear 1, ωp1 is the angular velocity of the large star gear, ωp2 is the angular velocity of the small star gear, ωs2 is the angular velocity of the sun gear 2, αw1 is the meshing angle of the 1st external meshing, αw2 is the meshing angle of the 2st external meshing, ɸi is the position angle of the i star gear relative to the first star gear, ɸi=2πi-1/n, n is the number of star gears, t is the time, and subscripts s1/p1i/p2i/s2, respectively, represent the sun gear 1, the first-stage star gear i, the second-stage star gear i, and the sun gear 2. The equivalent error of meshing error is analyzed along the two-stage external meshing line. Supposing that the center of the star gear 1 is on the x-axis, as shown in Figure 4, the direction of the equivalent meshing error out of the meshing line is defined as positive.Figure 3
Diagram of manufacturing error and assemble error.Figure 4
Calculation model of load sharing coefficient.


## 4.2. Comprehensive Angular Meshing Error

The accumulated meshing errors on the meshing lines of individual component can be obtained by superimposing meshing errors.(1)φs1p1i=φEs1i+φAs1i+φEbs1i+φEs1p1i+φAs1pi+φEbs1p1i+φbps1+φbpp1i+φts1+φtp1iφp2is2=φEs2i+φAs2i+φEbs2i+φEp2is2+φAp2is2+φEbp2is2+φbps2+φbpp2i+φts2+φtp2i.The comprehensive meshing error between theith star gear and the 1st-stage sun gear is Δφs1p1i0Ts1p1i, and the meshing error between the 2nd-stage sun gear and the ith star gear is Δφp2is20Tpis2.(2)Δφs1p1i0Ts1p2i=φs1i+φs1p1i+φp1iΔφp2is20Tp2is2=φs2i+φp2is2+φp2i.


## 5. Load Sharing Calculation Model of Two-Stage Star Gear Transmission System

Figure4 shows the load sharing calculation model of star gear transmission, which is made up of two parts. One is the model between the sun gear in the first stage and star gears, as shown in the first stage; the other is the model between the sun gear in the second stage and star gears, as shown in the second stage.All gears are considered as floating components. Meshing pair, rotation pair, and elastic deformation of the support are expressed in equivalent stiffness.Ks1p/Kps2 represent the meshing stiffness of the sun gear 1 and the star gear, the meshing stiffness of star gear, and sun gear 2. Ks1/Ks2/Kp1/Kp2 represent the support stiffness of the sun gear 1, the sun gear 2, the first-stage small star gear, and the second-stage large star gear, respectively. The input torque is Ts1. In the meshing pair s1p1i, the torque from big star gear to sun gear 1 is Ts1p1i. In the meshing pair p2is2, the torque from small star gear to sun gear 2 is Ts2p2i and Tij represents the acting torque from j gear to i gear.The drive torque is positive and the load torque is negative.Xs1/ys1 are the floating amount in x and y directions of the first-stage star gear and xs2/ys2 are the floating amount in x and y directions of the second-stage star gear. Xs2/ys2 are the floating amount in x and y directions of the second stage of sun gear. Ωp1i/Ωp2i are the coefficient of load sharing for the two-stage star gear; Ωp is the coefficient of load sharing for transmission system.Torque equilibrium conditions of transmission system are as follows:(3)Ts1+∑inTs1p1i=0Tp1is1+Tp2is2=0.i=1,…,nRelationship between acting torque and reaction torque is as follows:(4)Tp1is1=-rbp1irbsTs1p1i=0.Using formulas (3) and (4), formula (5) can be obtained. (5)Ts1+∑inTs1p1i=0i=1,…,n-rbp1irbs1Ts1p1i+Tp2is2=0.The meshing angle of each gear pair satisfies the following relationship:(6)Δφs1p1iTs1p1i=Δφs1-rbp1irbs1Δφp1iΔφp2is2Tp2is2=Δφp2i-rbs2rbp2iΔφs2.φ
i represents the rotation angle of the gear i, ΔφijTij represents an angle microdisplacement of the gear i with respect to the gear j, namely, the load transmission error. ΔφijTij is a function of Tij. The transmission errors of the ith meshing pair are converted into the equivalent angular meshing errors with respect to the sun gear 1:(7)Δφi=Δφs1p1i+rbp2irbs1Δφp2is2=Δφs1-rbs2rbp2iΔφs2.The power transmission error of each split is equal to the equivalent angular meshing errors of the sun gear 1: namely,Δφ1=⋯=Δφ3; the angular displacement coordination condition is as follows:(8)Δφs1p11Ts1p11+rbp2irbs1Δφp21s1Tp2is2=Δφs1p1iTs1p1i+rbp2irbs1Δφp21s2Tp2is2.Gear transmission error consists of the following two parts:(9)ΔφijTij=Δφij1Tij+Δφij0Tij.Δ
φ
i
j
0
(
T
i
j
) is the relative rotation angle of the initial interdentally space before the gear j and the gear i contacted (see in (5)); Δφij1(Tij) is the relative rotation angle of gear j and gear i after the deformation of the relative meshing point.(10)Δφij1Tij=FijKijri=TijKijri2(11)Δφs1p1i1Ts1p1i=Ts1p1iKs1prbs12Δφp2is21Tp2is2=Tp2is2Kps2rbp2i2.Using formulas (2), (8), and (11), meshing transmission error can be obtained. (12)Δφs1p1iTs1p1i=Ts1p1iKs1prbs12+φs1p1i+φs1iΔφp2is2Tp2is2=Tp2is2Kps2rbs22+φp2is2+φs2i.The equilibrium equation of transmission system involving the gear floating is as follows:(13)∑i=1nTs1p1irbs1cos⁡Ai+Ks1xs1=0∑i=1nTs1p1irbs1sin⁡Ai+Ks1ys1=0Ts1p1irbs1cos⁡Ai-Kp1xp1i=0Ts1p1irbs1sin⁡Ai-Kp1yp1i=0Tp2is2rbs2cos⁡Bi+Kp2xp2i=0Tp2is2rbs2sin⁡Bi+Kp2yp2i=0∑i=1nTp2is2rbs2cos⁡Bi+Ks2xs2=0∑i=1nTp2is2rbs2sin⁡Bi+Ks2ys2=0(14)Ωp1i=Ts1p1iTs1/ni=1,2,…,nΩp2i=Tp2is2rbp1i/rbp2iTs1/n.Using formulas (6), (9), (13), and (14), the average load sharing coefficient of star gear can be obtained:(15)Ωp=max⁡Ωp1i,Ωp2i.The more star gears, the bigger load sharing coefficient and the smaller dimension for radius of gearing system. If the load sharing coefficient of gearing system is much larger than 1, it means load sharing condition is not well, which makes the gear have enough strength margin which will cause the gearing system to became heavy. The aeroengine has a strict study of weight; load sharing coefficient equal to 1 is the ideal condition; this means meshing force of gearing system is equal in each star gear. At the same time, it also means not have unnecessary weight of gearing system.


## 6. Load Sharing Characteristics of Two-Stage Star Gear Transmission System

From the ideal center line position and shape tolerance standard (GB1182-1184-80), gear manufacturing and installation errors can be obtained, the location errors were taken as 6μm, and the phase was taken as 0.25°. Tooth thickness, pitch section, and bearing error are also taken as 6 μm, Ks1p=Kps2=1×107 N/m, Ks1=4×107 N/m, Ks2=8×107 N/m, Kp1=4×107 N/m, and Kp2=8×107 N/m.In the condition of all manufacturing and installation errors at the same time, the load sharing characteristics of system were shown in Figure5, and the load sharing coefficients of star gear were 1.0179, 1.0136, and 1.0619. The load sharing coefficient of system was 1.0619. The load sharing coefficient of gearbox for wind turbine at certain type is 1.088 [13], and the load sharing coefficient of gearing system for aeroengine is less than that of wind turbine, which also proves that the result is right because the level of precision for aeroengine is higher than wind turbine. Change rules of Ts1p1i, Tp2is2 are shown in Figures 6 and 7. Figures 8–11 show the floating orbit and floating amounts of the center gear.Figure 5
Load sharing curve of the first-stage star gear.Figure 6
Acting torque from big star gear of the first stage to sun gear 1.Figure 7
Acting torque from sun gear 2 to small star gear of the second stage.Figure 8
The floating orbit of first-stage sun gear (S1) and second-stage sun gear (S2).Figure 9
The floating orbit of first-stage sun gear (S1).Figure 10
The floating orbit of second-stage sun gear (S2).Figure 11
The floating amount of the sun gear.Figure5 is the load sharing curve for three star gears of first stage; load sharing coefficient of the first star gear is 1.0179, load sharing coefficient of the second star gear is 1.0136, and load sharing coefficient of the third star gear is 1.0619. The load sharing coefficients of three star gears are not the same which means the acting force of the three star gears is not the same. The load sharing coefficient is 1 in ideal condition, which means the acting force in each star gear is equal. In fact, acting force of the third star gear is the maximum value, and acting force of the second star gears is the minimum value.Figure6 is the acting torque curve from big star gear (p1i) of first stage to sun gear 1 (s1), acting torque of the first star gear in first stage (p11) is 8.2 Nm, acting torque of the second star gear in the first stage (p12) is 8.1 Nm, and acting torque of the third star gear in the first stage (p13) is 8.4 Nm. The acting torque of three star gears is not the same which means the acting force of the three star gears in the first stage is not the same. The acting torque of three star gears is the same in ideal condition, which means the acting force in each star gear is equal. In fact, acting force/acting torque of the third star gear is the maximum value, and acting force/acting torque of the second star gears is the minimum value.Figure7 is the acting torque curve from small star gear (p2i) of second stage to sun gear 1 (s2), acting torque of the first star gear in the second stage (p21) is 29.5 Nm, acting torque of the second star gear in the second stage (p22) is 29.2 Nm, and acting torque of the third star gear in the second stage (p23) is 30.2 Nm. The acting torque of three star gears is not the same which means the acting force of the three star gears in the second stage is not the same. The acting torque of three star gears is the same in ideal condition, which means the acting force in each star gear is equal. In fact, acting force/acting torque of the third star gear is the maximum value; the acting force/acting torque of the second star gears is the minimum value.Figure8 is the floating orbit of sun gear in the first stage and second stage; the floating orbit of sun gear in the first stage (s1) in Figure 8 is blue, and the floating orbit of sun gear in the second stage (s2) in Figure 8 is black. The floating orbits of sun gear in the first stage (s1) and sun gear in the second stage (s2) do not intersect and overlap. The floating orbit scope of sun gear in the first stage (s1) is from −1.85 × 10−5 m to −1.7 × 10−5 m in X direction; the floating orbit scope of sun gear in the first stage (s1) is from 4.5 × 10−6 m to 7.5 × 10−6 m in Y direction. The floating orbit scope of sun gear in the second stage (s2) is from 0.83 × 10−5 m to 0.91 × 10−5 m in X direction; the floating orbit scope of sun gear in the second stage (s2) is from 2.6 × 10−6 m to 4.2 × 10−6 m in Y direction.Figures9 and 10 are the enlarged drawing for floating orbit of first-stage sun gear (s1) and second-stage sun gear (s2), respectively. From the enlarged drawing, we can know that the floating orbit is not the single orbit, there are total of 4 orbits, and the floating orbit is not a standard circle, just like ellipse; the orbit transfers with the rotation.Figure11 is the floating displacements of sun gear of the first stage and second stage (s1 and s2) in each direction. Floating displacement value of sun gear 1 of the first stage (s1) in x direction is −1.8 × 10−2 mm and floating displacement value of sun gear 1 of the first stage (s1) in y direction is 0.7 × 10−3 mm. Floating displacement value of sun gear 2 of the second stage (s2) in x direction is 0.9 × 10−2 mm and floating displacement value of sun gear 2 of the second stage (s2) in y direction is 0.3 × 10−3 mm.


## 7. Conclusion

The eccentricity error, installation error, tooth thickness error, pitch section error, manufacturing error of all bearings, and floating meshing error of all gears in the two-stage star transmission system are considered in this model and the integrated angular meshing error of the two-stage external meshing line is obtained finally.Based on the coordinated condition of angular displacement and the condition of torque balance, load sharing models of 3-road power splitting for 2-stage external meshing star gear transmission system are established. The model reflects the load sharing process caused by the load deformation of gears and the essential characteristics of the coordination of the gear corners in the power split system.The load sharing coefficient, variation law of torque, and numerical value are obtained, which are consistent with all floating and angular displacements of gears. The floating law of the two-stage sun gear is obtained. The floating locus of input sun gear is obviously larger than that of output sun gear. And the two floating orbits do not overlap and intersect, the floating orbit is not a single trajectory, the floating amount of center gears inx direction is larger, and the floating amount of sun gear 1 is larger than sun gear 2 in the corresponding direction.



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*Source: 1037479-2017-12-27.xml*