外文資料-design and development of few-tooth-deference planetary gear powertrain

1、IEEE Vehicle Power and Propulsion Conference (VPPC), September 3-5, 2008, Harbin, China 978-1-4244-1849-7/08/$25.00○ C 2008 IEEE Design and Development of Few-Tooth- Deference Planetary Gear Powertrain Coupling System w

2、ith Biased Bent Shaft in Electric and HEV for All-Terrain Vehicles Wang Yong-bin Zhang Zeng-nian Chen Wen-xin Yang Ya-ping Liang Feng Tu Xiao-feng Shi Yi-ping Zhang Xin Li Chang-gang Zhejiang Wanli University

3、 / School of Electronic and Information Engineering, Ningbo City, P.R.China. Email: wyb@zwu.edu.cn Abstract—The article has analyzed the domestic and international present research status and development trend of the e

4、lectric and hybrid electric vehicles (HEV). Considering actual scientific research, according to the characteristic and environment requirement of all-terrain vehicle（ATV）, the principle of elected and designed compo

5、nent parts for Powertrain Coupling system of ATV, and the demands of performance parameter of power, torque and speed of moving ATV, this article studies on the performance parameter and control strategy of powertrain

6、 coupling system of engine, electric motor and the storage battery. The optimization matching, the modeling simulation and the experiment have been carried out. The article proposes a new multipurpose design and dev

7、elopment plan on the powertrain coupling system in electric and HEV for ATVs. It introduces a new transmission system based on few- tooth - deference planetary gear powertrain coupling system with biased bent shaft （

8、FPS）, which have been applied in powertrain coupling system of the multipurpose light electric and HEV for ATV. The research results show that the proposed FPS meets the performance requirement for entire vehicle

9、 （ATV）, especially in regard infinitely variable speed. The method and the obtained result provide the basis design theory for the low-speed vehicles (that is, agricultural vehicles) and multipurpose light electric

10、 and HEVs. The technology has been applied to ATVs in Ningbo Saiting Electric Bicycle Science powertrain coupling system; few- tooth - deference planetary gear transmission; optimize matching I. INTRODUCTION UP to

11、 the present, the low-speed vehicles and ATV yet not used the technology of the electric and HEV. According to low-speed vehicles and ATV of HEV in road, environment, speed and load situations, through the engine, th

12、e rechargeable battery and the electric motor/generator optimal fit, it studies one kind design and development plan of the new powertrain coupling system in electric and HEV for ATV. It focal introduces the new tran

13、smission set based on the FPS, which have applied in powertrain coupling system of the multipurpose light electric and HEV for ATV, it emphasis introduces its application. Because the FPS have merits of the stru

14、cture compact, the velocity ratio big, the efficiency high, the revolution steady, bearing capacity strong, the processing simple, the cost low status. It may apply in the ATV, the national defense, the metallurgy, t

15、he mine; lifts heavy objects professions and so on transportation, measuring appliance manufacture, etc[1]. The FPS may enhance the engine working efficiency, save the energy, discharge cleanly, and reduce the enviro

16、nmental pollution and so on. This kind of vehicle besides the engine can charge to the battery, the power can be regenerated to battery when vehicle is in deceleration, the brake can transform mechanical energy to e

17、lectrical energy avoiding the energy waste. With the HEV, the fuel efficiency of vehicle may enhance one time compared to the ordinary vehicle, simultaneously changes CO2 withdrawal to one half, which lead the earth

18、to warm. It is innovative that the ATV uses the HEV technology, and the breakthrough point of infinitely variable speed is appropriate. Having the broad market application prospect, this technology also may be used i

19、n the ATV, and it will have huge development potential and favorable market prospect. The designing and developing light electric and hybrid electric vehicles E number of teeth za and zb; module mn; graduated circle

20、 helix angleβ; facewidth ba and bb; speed ratio i45 of FPS with low speed level; module m; number difference of teeth zd; number of teeth z3 and z4; stand-off coefficient y3 and y4; addendum coefficient ha*; working pr

21、essure angleα′; facewidth b3 and b4. Among the variable up, the independent design variable have i12 、za 、mn 、β、b1 、m 、zd 、z3 、y3 、y4 、b3. Therefore, the design variable[18,19,20] is X = [ iab, za , mn ,β, b1 , m ,

22、 zd , z3 , y3 , y4 , ha*, b3 ]T = [ x1 , x2 , x3 , x4 , x5 , x6 , x7 , x8 , x9 , x10 , x11 ,x12 ]T C. Objective function Uses the FPS in the ATV mainly are in order to obtain the small structure size. Therefore, the mos

23、t research single target is optimizing by the structure volume for smallest. In order to calculate conveniently, it usually takes various gears reference volume as computation basis. Thus, first, addendum coefficient

24、 ha*, stand-off coefficient y3 and y4; working pressure angle α′ and so on parameters cannot reflect in the objective function, but these parameters have the reflection in constraint condition, such as tooth profile

25、 overlap interference, pinion transition curve interference and contact ratio. If depends on the experience to determine them, sometimes causes not to be able to satisfy the constraint condition. Second, in order to

26、satisfy the FPS tooth profile not to overlap the interference condition, the transmission generally uses clockwise drive and simultaneously reduces addendum coefficient ha*，but uses the clockwise drive can cause the t

27、ransmission working pressure angle α′ to increase, and causes the crankshaft bearing radial force to increase, thus affects the bearing life and the transmission efficiency [4,5]. In the FPS design, the working pressur

28、e angle α′is an important parameter must take a more appropriate value. In order to cause the transmission device weight to be light, the volume is small, has high transmission efficiency, and has high service life,

29、this article take the various gears volume sum is smallest and the working pressure angle α′is smallest as the double optimized goal[4,5], namely invα′= invα+2 ( y4 - y3)/zd × tanα （5） In the formula invα= tanα

30、-α, α is the pressure angle of reference circle. V = V1 + V2 + V3 + V4 =π/4×( da1 2 b1 + 2 da22 b1 + 2 df32 b3 + da42 b3)（6） In the formula, da1 、da2 、da5 respectively are the tip diameter of gear 1、2 and 5; df3 is

31、 the root diameter of gear 3.The objective function is f ( X) =ω1 (invα′/ invα*′) +ω2 ( V/ V* ) （7） In the formula, ω1 、ω2 are the weighting factor, takesω1 = 1, ω2 = 2, expression the volume for main optimized goal, an

32、d the working pressure angle for secondary optimized goal; α*′、V * respectively is the working pressure angle and the volume empirical value. D. Constraint Condition 1) The constraint condition of movement performa

33、nce a) The limiting condition of tooth profile overlap interference of internal and external gear , g1 ( X) : z5 (invαa4 +δ2) - z3 (invαa3 +δ1) +( z5 - z3) ×invα′≤0 ' 32 ' 2324 1 1 2 cos αα δaa a rr r + ? =

34、 ?' 42 ' 2324 1 2 2 cos αα δaa a rr r + ? = ?In the formula, a′is a center distance of the gear 3 and 5. b) The limiting condition of inner engagement contact ratio g2 ( X) : z3 [ (tanαa3 - tanα′) - z5 (tanαa4 –

35、 tanα′) ]/ 2 π ≥ 1. 05 c) The limiting condition of transition curve interference of inner and annular gear g3 ( X) : z3tanαa1 + ( z5 - z3) tanα′- ( z5 -z0)× tanα04′- z0tanαa0 ≤ 0 In the formula, z0 is the tooth n

36、umber of internal gear tooth slotting tool, αa0 is the working pressure angle of tip circle of internal gear tooth slotting tool, α04′is working pressure angle between internal gear tooth slotting tool and inner gear.

37、d) The interference limiting condition of inner gear top cut g4 ( X) :1 - z3/ z5 - tanαa4/ tanα′≤ 0 e) The interference limiting condition of inner gear under cut g5 ( X) : ha*- z5sin2α/ 2 - y4 ≤ 0 f) The limiting co

38、ndition of apex clearance of inner gearing gear g6 ( X) : ra3 - rf4 + c*m ≤ 0 2) Constraint condition of intensity a) The limiting condition of contact fatigue strength of flank of tooth g7 ,8 ( X) :[σ] H1、3σH1、3- 1 ≥