# A CAD Design of a New Planetary Gear Transmission

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2 satellite 5 will be unlocked by overcoming frictions at teeth contacts. A kinematic characteriation of the mechanism can be expressed as function of parameters of external torques M, M H2 on the carriers and constant input angular velocity ω as pointed out in [5,6], (Figure 1). The kinematic relations among the angular velocities of the s with 1, 2,, 4, 5, 6 teeth can be expressed in the form 1 ( ) 1 u 1 H 2 ( H 2) 46 Where H 2 u ( 1) u H 1 1 (1) (2) ( 2) 6 u H 46 () 4 M M (4) H 2 / H 2 when i are the number of teeth in the (i=1,..,6). From Eqs. (1) and (2) angular velocities ω, ω 1 of s and 1 can be obtained as ( u 1) ( u 1) ( ) ( H2) 1 46 H2 ( ) ( H2) (5) u1 u46 ( ) u ( ) 1 1 (6) Figure 1 A kinematic scheme of the new planetary Internal reaction forces R 12, R 2, R 45 and R 56 on points D, C, G, E in Figure 1 can be expressed for static equilibrium by conditions through external forces F and R H2. An external input force F is applied to a point B and a reaction force R H2 is applied to a point K. A scheme for static equilibrium for force F is shown in Figure 2 (a) and for the reaction force R H2 is shown in Figure 2 (b). (a) (b) Figure 2 A scheme for static equilibrium: a) for the input link; b) for the output link. and output powers can be expressed in form W W input M output M H 2 H 2 (7) (8) Efficiency of the mechanism can be expressed in form M M (9) H 2 H 2 / A numerical example can be carried out for an application for a wind turbine. Assuming from wind flow ω =150 rpm and M = 12 Nm; M H2 = 15 Nm, (Figure 1), the output and intermediate angular velocities ω H2, ω 1, ω and internal forces can be computed with the proposed model through Eqs. (1) to (6) by considering ω 4 = ω 1, ω 6 = ω. From Eq. (4) angular velocity of output carrier is computed as ω H2 = 75 rpm. From Eqs. (5) and (6) angular velocities of s 1 and are computed as ω 1 =250 rpm and ω =50 rpm, respectively. III. A CAD MODEL The proposed differential planetary box consists of a mechanical planetary set without additional devices such as torque converters or electronic parts. 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 10-0 m/s, An example of a wind turbine with a proposed planetary box is presented in Figure All rights Reserved. Page 1064

4 Figure 8 A CAD design of the input and output epicyclic s: a) cross-section view: 1-input epicyclic internal ; 2-output epicyclic internal ; -wheel; b) general view. Figure 9 shows a scheme for assembly of planetary box with the following main components as an input carrier, input satellite, spindles of input and satellites, input and output epicyclic internal s, shift (output sun ), input sun ; output carrier, bearings of support, bearings of epicyclic internal s and bearings of input and output carriers. main dimensions can be as equal to a maximum high D (in Figure 10 a) of 180 mm, a maximum longitudinal sie L (in Figure 10 a) of 110 mm and maximum width W (Figure 10 b) of 150 mm. The input and output shafts have a diameters of 2 mm and 0 mm, respectively. The overall weight is 9 kg without lubrication element. In order to decrease a friction at teeth contacts it is necessary to use a lubricant. The most common current lube such as 75W90 GL5 can be used for this planetary transmission. All the s are made from steel 40Cr. The pressure angle of s is 20 degrees. Another parts such as carriers, axis, wheel, housing, cover and frame are made from steel C45. The mechanism has also standard fastening components such as bolts, nuts, screws and bearings. All the geometrical parameters of s of the planetary transmission are listed in Table 1. Figure 9 A scheme for assembly of a planetary box: 1- output carrier; 2- bearing; - output satellite; 4- axis of output satellite; 5- bearing of shaft; 6- bearing of epicyclic internal s; 7- output sun ( shaft); 8- input sun ; 9- wheel; 10- input satellite; 11- axis of input satellite; 12- input carrier. IV. A MECHANICAL DESIGN OF A NEW PLANETARY GEAR BOX A mechanical design of a new planetary transmission with planetary set has been worked out in Solid Works software. Figure 10 shows a full mechanical design with a housing and cover of planetary transmission with the following main components such as an input carrier, bearings, housing, shaft with output sun, output satellite, input and output epicyclic internal s, input satellite, cover, input sun, output carrier, axis of satellites, supports with frame and other standard fastenings. All the geometrical parameters have been defined within the CAD model as referring to an application for small wind turbine installation. The a) b ) Figure 10 A mechanical design of a new planetary box with design sies: a) crosssection view: 1-output carrier; 2-bearing; - housing; 4- shaft with output sun ; 5-output satellite; 6-epicyclic internal s; 7-input satellite; 8-bearing; 9-sun ; 10-input carrier; b) longitudinal view. Table 1 The geometrical characteristics of s of a new planetary Gear sun satellite internal sun Number of teeth Nominal shaft diameter (mm) Overall length (mm) Quantity All rights Reserved. Page 1066

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