The aim of the paper is to present a planetary gearbox for wind turbine. At constant wind power input the planetary gearbox is able to provide variable speed of the output shaft. The main purpose of the differential transmission is on the capability to adapt the operation to variable loading of wind. A CAD model has been proposed in order to investigate the operation feasibility of the proposed design solution. A proper dynamic model has been developed in ADAMS software. Simulation tests have been carried out and results are discussed to validate the proposed design solution

Algazy Zhauyt

Beibit Shingissov

Gani Balbayev

Shynar Kurmanalieva

Zhanar Koishybayeva

English

Vibroengineering PROCEDIA

 24 © JVE INTERNATIONAL LTD. VIBROENGINEERING PROCEDIA. OCT 2015, VOLUME 6. ISSN 2345-0533  
Numerical check of a 2DOF transmission for wind 
turbines 
Beibit Shingissov1, Gani Balbayev2, Shynar Kurmanalieva3, Algazy Zhauyt4,  
Zhanar Koishybayeva5 
1, 2Almaty University of Power Engineering and Telecommunication, Almaty 050013, Kazakhstan 
1, 3, 4, 5Department of SC&TMTB, Kazakh National Technical University, Almaty 050013, Kazakhstan 
1Corresponding author 
E-mail: 1beibit_tumen@mail.ru, 2gani_b@mail.ru, 3shinarshinara_kurmanal@mail.ru, 
4ali84jauit@mail.ru, 5zhanarbi@rambler.ru 
(Accepted 3 September 2015) 
Abstract. The aim of the paper is to present a planetary gearbox for wind turbine. At constant 
wind power input the planetary gearbox is able to provide variable speed of the output shaft. The 
main purpose of the differential transmission is on the capability to adapt the operation to variable 
loading of wind. A CAD model has been proposed in order to investigate the operation feasibility 
of the proposed design solution. A proper dynamic model has been developed in ADAMS 
software. Simulation tests have been carried out and results are discussed to validate the proposed 
design solution. 
Keywords: gearbox, gears, simulations, wind turbines, ADAMS software. 
1. Introduction 
Gearboxes are used in various types of industrial machinery to provide suitable torque while 
reducing speed from a rotating power source by using gear ratios. Gearboxes are used in many 
applications, such as wind turbines, conveyors, draglines, bridges and many other machines. Gears 
also are used in differential drives of automobiles, final drives of tractors and heavy machineries 
mainly as reducer. The efficiency of gear trains depends on many factors such as the type and 
profile of teeth profile, contact stresses, number and type of bearings. These factors have been 
studied with recent approaches in [1-4]. Planetary gear transmissions are commonly used in 
applications where a large speed reduction is required as pointed out in [4, 5]. Several design 
solutions have been proposed in the literature, like for example in [6-10]. General design 
characteristics have been selected for practical applications of the transmission, like for example, 
in wind turbine installations. A wind turbine installation can be identified by referring to a small 
wind turbine of 10 kW power and with average wind speeds of 10-25 m/s.  
2. A kinematic model of a new planetary gearbox 
The proposed new planetary transmission can be considered as a CVT (solution). It consists 
of a mechanical planetary gear set. In this research work a new solution is considered for 
improving the efficiency of planetary transmissions. This mechanism has two mobile planetary 
gear sets with an asymmetrical design, Fig. 1. The asymmetrical design gives special operation 
features. The special operation features can be recognized in smoothly changing reduction ratio 
depending on the load of output shaft. A kinematic characterization of the mechanism can be 
expressed as function of parameters of external torques ܯுଵ, ܯுଶ on the carriers and constant 
input angular velocity ߱ுଵ,, Fig. 1. The kinematic relations among the angular velocities of the 
gears with 1, 2, 3, 4, 5, 6 teeth can be expressed in the form: 
߱ଵ − ߱ுଵ
߱ଷ − ߱ுଵ = ݑଵଷ
(ுଵ), (1) 
߱ଵ − ߱ுଶ
߱ଷ − ߱ுଶ = ݑସ଺
(ுଶ), (2) 
NUMERICAL CHECK OF A 2DOF TRANSMISSION FOR WIND TURBINES.  
BEIBIT SHINGISSOV, GANI BALBAYEV, SHYNAR KURMANALIEVA, ALGAZY ZHAUYT, ZHANAR KOISHYBAYEVA 
 © JVE INTERNATIONAL LTD. VIBROENGINEERING PROCEDIA. OCT 2015, VOLUME 6. ISSN 2345-0533 25 
where ݑଵଷ(ுଵ) = − ݖଷ ݖଵ⁄  and: 
ݑସ଺(ுଶ) = −
ݖ଺
ݖସ, (3)
߱ுଶ =
ܯுଵ߱ுଵ
ܯுଶ , (4)
when ݖ௜ are the number of teeth in the gear (݅ = 1,.., 6). From Eqs. (1) and (2) angular velocities 
߱ଷ, ߱ଵ of gears 3 and 1 can be obtained as: 
߱ଷ =
൫ݑଵଷ(ுଵ) − 1൯߱ுଵ − ൫ݑସ଺(ுଶ) − 1൯߱ுଶ
ݑଵଷ(ுଵ) − ݑସ଺(ுଶ)
, (5)
߱ଵ = ݑଵଷ(ுଵ)(߱ଷ − ߱ுଵ) + ߱ுଵ. (6)
 
Fig. 1. A kinematic scheme for the new planetary gear box: longitudinal view with ܪଵ – input carrier,  
1 – input sun gear, 2 – input satellite, 3 – input epicyclic gear, 4 – output sun gear, 5 – output satellite,  
6 – output epicyclic gear, ܪଶ – output carrier 
3. Adams model 
Virtual design of the proposed planetary gearbox with 2-DOFs has been done in ADAMS 
software. An input angular velocity and output torque have been specified. The constant speed of 
motor with value of 400 rpm has been applied to the input carrier. An external torque with a 
constant value of 45 Nm has been applied to the output shaft of planetary gearbox. The proposed 
design of planetary gear transmission is shown in Fig. 2. Simulation of the gearbox has been 
proposed in order to investigate the engineering feasibility of the proposed design solution. The 
main dimensions can be as equal to a maximum high of 150 mm, a maximum longitudinal size of 
200 mm and maximum width of 160 mm. The pressure angle of teeth of gears is 20 degrees. All 
gears are made from steel Cr 40 and carriers, spindles, shafts are made from steel C45, except 
standard parts such as bearings, washers, nuts, bolts and screws. The gears have been made with 
module of 1 mm. The output and input shafts have different diameters of 14 and 30 mm 
correspondingly. 
4. Simulation modes 
Input parameters for the simulation of a planetary gear transmission have been defined. Input 
angular speed of motor and torque have been given as a constant values of 400 rpm and 15 Nm. 
Output torque is variable in range from 1 up to 8 Nm. Friction coefficient of gears has been set as 
equal to 0.2 by referring to a contact of steep surfaces. Table 1 shows main other parameters that 
have been assumed by referring to feasible values for a real case of study considering material, 
NUMERICAL CHECK OF A 2DOF TRANSMISSION FOR WIND TURBINES.  
BEIBIT SHINGISSOV, GANI BALBAYEV, SHYNAR KURMANALIEVA, ALGAZY ZHAUYT, ZHANAR KOISHYBAYEVA 
26 © JVE INTERNATIONAL LTD. VIBROENGINEERING PROCEDIA. OCT 2015, VOLUME 6. ISSN 2345-0533  
penetration depth and force exponent. 
During the simulation of model the output parameters such as angular velocity, torque contact 
forces have been computed in order to investigate the dynamic behavior of the proposed 
transmission. Tests have been carried out by considering a constant input speed as 400 rpm and 
torque as 15 Nm and variable output torque as 1-8 Nm. When a variable torque is applied to the 
output shaft of planetary gearbox the input shaft has to rotate continuously with the constant speed 
of motor of 400 rpm. If this process will happen then it means the planetary gear box works with 
2 degrees of freedom and changes reduction ratio. 
 
Fig. 2. The ADAMS model of the final design with reference frames and applied loads 
Table 1. Input parameters for simulation of model in Fig. 2 
Parameter Valve Units 
Input angular velocity 400 rpm 
Input torque 15 Nm 
Output angular velocity Plots in Fig. 3 rpm 
Output torque Variable (1-8) Nm 
Damping 10 N∙sec/mm 
Young’s modulus 2.07 E+005 N∙mm2 
Density 7.801 E-006 Kg/mm3 
Penetration depth 0.1 mm 
Force exponent 1.8  
5. Simulation results 
The variable torque has been applied in order to check feasibility of change reduction ratio 
automatically. The proposed planetary gear transmission can to adapt to externally applied 
variable load to the output shaft by smoothly changing reduction ratio. In this paper, dynamic 
simulations are carried out with the aim to check the feasibility of the proposed gearbox for wind 
turbine installation. The results of dynamic simulation have been obtained and presented in the 
plots of Figs. 3 to 8.  
Angular velocities of the input and output shafts of planetary gear transmission are presented 
in Fig. 3. The input angular velocity has been given as a constant speed of motor of 400 rpm. As 
shown in the plot of Fig. 3 the input angular speed is constant during the test. The output angular 
velocity with approximately average value of 425 rpm is presented in Fig. 3 (red line). By 
considering the plot in Fig. 3 the output speed changes from 400 up to 450 rpm during the test. 
This is because, the variable torque has been applied to the output shaft of gearbox. The generated 
variable torque is presented in Fig. 4. MSC ADAMS generates cyclic different values of torque 
from 1 up to 8 Nm during the test. This torque change affects to the output angular velocity. The 
input shaft of the planetary gear transmission rotates with constant speed and it can be observed 
in Fig. 3 and 4. Fig. 5 shows the plot of computed angular velocities of the input and output sun 
NUMERICAL CHECK OF A 2DOF TRANSMISSION FOR WIND TURBINES.  
BEIBIT SHINGISSOV, GANI BALBAYEV, SHYNAR KURMANALIEVA, ALGAZY ZHAUYT, ZHANAR KOISHYBAYEVA 
 © JVE INTERNATIONAL LTD. VIBROENGINEERING PROCEDIA. OCT 2015, VOLUME 6. ISSN 2345-0533 27 
gears (red and blue dot lines). The input and output sun gears rotate with same angular speeds. 
Results show that the angular speeds of sun gears change from 450 up to 500 rpm during the 
simulation. Computed torque of the sun gear is presented in Fig. 6. The torque change from 1 up 
to 4 Nm. The curve in the plot is cyclic. Computed plot of the angular speed of the input planet 
gears is presented in Fig. 7. The angular velocity of input planet gears is approximately 375 rpm. 
Fig. 8 shows computed plot of angular speeds of output planet gears. The speed changes from 225 
up to 350 rpm and curve in the plot is cyclic.  
 
Fig. 3. Computed plot of the angular speed of the input and output shafts  
   
Fig. 4. Applied variable torque to the output shaft  
 
Fig. 5. Computed plot of the angular speed of the input (blue line) and output (red line) sun gears 
The variable load which has been applied to the output shaft is cyclic as shown in Fig. 4 and 
this cyclic load affected to the output results. By considering Figs. 3-8 it is possible to say the 
planetary gearbox can adapt to external applied load. The input shaft rotates constant angular 
speed. The smoothly cyclic curves in the plots show that the system can smoothly change 
reduction ratio.  
By considering these results of study of a planetary gearbox with a virtual models it is possible 
to identify that the mechanism can adapt to a variable external load. The simulation results show 
that the proposed planetary gearbox has suitably output parameters both in terms of speed and 
torque. Results with the preliminary model show that the gearbox has a constant output values, 
NUMERICAL CHECK OF A 2DOF TRANSMISSION FOR WIND TURBINES.  
BEIBIT SHINGISSOV, GANI BALBAYEV, SHYNAR KURMANALIEVA, ALGAZY ZHAUYT, ZHANAR KOISHYBAYEVA 
28 © JVE INTERNATIONAL LTD. VIBROENGINEERING PROCEDIA. OCT 2015, VOLUME 6. ISSN 2345-0533  
when the constant load has been applied to the system. Results with the final model of planetary 
gear transmission show that the planetary gear box has capability to adapt to a variable load. In 
this study simulation results show that the gearbox smoothly changes the reduction ratio at 
constant input speed. It means the input shaft rotates with a constant angular speed of motor.  
 
Fig. 6. Computed plot of the torque of the sun gears 
 
Fig. 7. Computed plot of the angular speed of the input planet gears 
 
Fig. 8. Computed plot of the angular speed of the output planet gears 
6. Conclusion 
A planetary gear box with two degrees of freedom has been studied from aspects of mechanical 
design and kinematic modeling. A mechanical design and 3D CAD model of a planetary gear box 
with two degrees of freedom have been proposed in order to adapt the operation to variable  
loading. Design of the planetary gearbox is shown in kinematic scheme. In order to check the 
feasibility of the design a dynamic simulation of the planetary gearbox has been carried out in 
ADAMS software. Simulation results show that the proposed planetary gear box has suitably 
constant output values both in terms of speed and torque. The simulation results also show that 
the proposed gear box smoothly changes the reduction ratio at constant input speed. The main 
achievement of this work is the new design for a new planetary gearbox with 2DOFs which can 
generate a variable reduction ratio. Results are suitable for using the proposed design in wind 
NUMERICAL CHECK OF A 2DOF TRANSMISSION FOR WIND TURBINES.  
BEIBIT SHINGISSOV, GANI BALBAYEV, SHYNAR KURMANALIEVA, ALGAZY ZHAUYT, ZHANAR KOISHYBAYEVA 
 © JVE INTERNATIONAL LTD. VIBROENGINEERING PROCEDIA. OCT 2015, VOLUME 6. ISSN 2345-0533 29 
turbine applications. 
References 
[1] Fetvaci C. Definition of involute spur gear profiles generated by gear-type sharper cutters. Mechanics 
Based Design of Structures and Machines, Vol. 38, Issue 4, 2010, p. 481-492. 
[2] Kaharman A., Ding H. A methodology to predict surface wear of planetary gears under dynamic 
conditions. Mechanics Based Design of Structures and Machines, Vol. 38, 2010, p. 493-515. 
[3] Patel P. Design and Analysis of Differential Gearbox. Report, U.V. Patelcolliege of Engineering, 
Ganpat University, Kherva, 2009. 
[4] Thirumurugan R., Muthuveerappan G. Critical loading points for maximum fillet and contact 
stresses in normal and high contact ratio spur gears based on load sharing ratio. Mechanics Based 
Design of Structures and Machines, Vol. 39, Issue 1, 2011, p. 118-141. 
[5] Muni D. V., Muthuveerappan G. A comprehensive study on the asymmetric internal spur gear drives 
through direct and conventional gear design. Mechanics Based Design of Structures and Machines, 
Vol. 37, Issue 4, 2009, p. 431-461. 
[6] Balbayev G., Ceccarelli M. Design and characterization of a new planetary gear box. Mechanisms, 
Transmissions and Applications, Mechanisms and Machine Science, Vol. 17, 2013, p. 91-98. 
[7] Balbayev G., Carbone G. A dynamic simulation of a novel continuous variable transmission. 
Proceedings of the 11th IFToMM International Symposium on Science of Mechanisms and Machines, 
Vol. 18, 2013, p. 109-116. 
[8] Carbone G., Mangialardi L., Bonsen B., Tursi C., Veenhuizen P. A. CVT dynamics: theory and 
experiments. Mechanism and Machine Theory, Vol. 42, 2007, p. 409-428. 
[9] Derek F. L., Dennis W. H. The operation and kinematic analysis of a novel cam-based infinitely 
variable transmission. ASME International Design Engineering Technical Conferences and 
Information in Engineering Conference, Philadelphia, Vol. 3, 2006, p. 1-6. 
[10] Yaghoubi M., Mohtasebi S. Design and simulation of a new bevel multi-speed gearbox for automatic 
gearboxes. Science Journal Report and Opinion, Vol. 2, 2010, p. 1-7. 


Numerical check of a 2DOF transmission for wind turbines

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Numerical check of a 2DOF transmission for wind turbines

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