外文翻譯--機床主軸傳動齒輪箱的優(yōu)化設計（英文）

1、ORIGINAL ARTICLEOptimal machine tool spindle drive gearbox designD. R. Salgado & F. J. AlonsoReceived: 4 August 2006 /Accepted: 23 March 2007 /Published online: 4 May 2007 # Springer-Verlag London Limited 2007Abstrac

2、t Many machine tools are equipped with a motor- gearbox to extend the constant power range of the machine tool spindle drive motor at low speeds. Currently, in the latest spindle drive motor technology, the gearboxes are

3、 integrated in-line between the water-cooled motor and the spindle inside the machine tool’s ram. The functionality of a spindle gearbox depends directly upon its constructional solution, and on the kinetic energy corres

4、ponding to this solution. In this work, spindle gearboxes are optimized taking this design factor into account. In the authors’ opinion, the results could be of great interest for spindle drive gearbox manufacturers.Keyw

5、ords Spindle gearbox design . Optimal design .Minimum kinetic energy. OptimizationNomenclature σH Hertz contact stress σF Bending stress σHP Allowable Hertz contact stress σFP Allowable bending stress σHO Nominal Hertz c

6、ontact stress σFO Nominal bending stress σHlim Maximum allowed Hertz contact stressσFlim Maximum allowed bending stress α Pressure angle Ft Tangential gear force b Face width β Helix angle d Pitch diameter m Module KA Ap

7、plication factor KHa trans. load sharing factor for pitting resistance KHb long. load sharing factor for pitting resistance KFa trans. load sharing factor for bending strength KFb long. load sharing factor for bending st

8、rength YFa Form factor for bending strength YNT Life factor for bending strength YRrelT Relative rugosity factor YSa Stress concentration factor YST Stress concentration factor YX Size factor for bending strength YdrelT

9、Notch relative sensitivity factor Y“ Contact ratio factor for bending strength Yb Helix angle factor for bending strength ZE Material factor ZH Geometry factor for pitting resistance ZL Viscosity factor ZN Life factor fo

10、r pitting resistance ZR Rugosity factor for pitting resistance ZV Velocity factor ZW Hardness ratio factor ZX Size factor for pitting resistance Zb Helix angle factor for pitting resistance Z“ Contact ratio factor for pi

11、tting resistance KV Dynamic factor Np Number of planet gears KE Kinetic energy of planetary system ωi Angular speed of gear iInt J Adv Manuf Technol (2008) 37:851–860DOI 10.1007/s00170-007-1028-6D. R. Salgado (*) Departm

12、ent of Electronics and Electromechanical Engineering, University of Extremadura, Sta. Teresa de Jornet 38, 06800 Mérida, Spain e-mail: drs@unex.esF. J. Alonso Department of Electronics and Electromechanical Engineer

13、ing, University of Extremadura, Avda. Elvas s/n, 06071 Badajoz, Spainratios. In particular, the two spindle gearbox configurations used by manufacturers are studied for all the marketed range of powers and speed ratios,

14、and the optimal designs of these configurations are given and compared for all that range.2 Considerations on the design of spindle drive gearboxesIn this section we explain some important considerations that must be tak

15、en into account for spindle gearbox design. The members of PGTs are of three types, depending on their movements and links with other members. In the present work, they will be called suns, arms, and planets. Two differe

16、nt PGT configurations are used by spindle gearbox manufacturers. They are shown in Fig. 2a and b. In these figures, members 1 and 2 are the suns, 3 is the arm, and 4 and 4′ are the planets.2.1 Economic and operating cons

17、iderationsThe spindle gearbox configuration of Fig. 2b has the advantage of being more interesting economically, since it does not include a ring gear. The reason is that spindle gearbox gears must be hardened, tempered,

18、 and ground to avoid high heating, and a ground ring gear is more expensive than a non-ground ring gear. Also, if the ring gear is not ground, heat buildup will occur more quickly, and this heating limits and reduces the

19、 input speed and torque.2.2 Efficiency considerationsAnother interesting consideration in spindle gearbox design is that it is possible to prove that the efficiency of the reducers based on these two PGT configurations i

20、s greater if they are designed with the input being the sun member. This is why all spindle gearboxes are designed as reducerPGTs with the sun (member 1) as input and the arm (member 3) as output, as shown in Fig. 2a and

21、 b.2.3 Planet member considerationsIn spindle gearbox design, it is quite important to choose an optimal number of planets for the required power and speed ratio. In this context, the number of planet members in a PGT (N

22、p) is the number of these members that are arranged around the PGT’s principal axis. For example, the com- mercial spindle gearbox shown in Fig. 2c has two planet members, i.e., Np=2. This number must be as small as poss

23、ible to reduce the weight and the kinetic energy of the transmission, while ensuring a good distribution of the load to each of the planet gears. This number can be two, three, four, or even more, depending on the applic

24、ation. Which- ever the case, the planets must always be arranged concentrically around the PGT’s principal axis to balance the mass distribution.3 The formulation of constraints in spindle gearbox designThis section desc

25、ribes the constraints in spindle gearbox design. They are grouped into three sets, according to the type of constraint. These are:– Constraints involving gear size and geometry – Planetary gear train meshing requirements

26、 – Contact and bending stresses3.1 Constraints involving gear size and geometryThe first constraint is a practical limitation in the range of acceptable face widths b. This constraint is as follows:9m ? b ? m ð1

27、2;where m is the module.Input member Output memberInput memberOutput membera b cFig. 2 a, b, Constructional so- lutions of the PGTs used to extend the constant power range. c An example of spindle gearbox based on th