Gear box

FIELD: mechanical engineering.

SUBSTANCE: gear box comprises input and output shafts, three planet gears, two clutches, and three brakes. Input shaft (2) is provided with solar pinion (3) of the second planet mechanism. Epicycle (5) of the planet mechanism is connected to carrier (6) of the first planet mechanism and brake (18). Epicycle (8) of the first planet mechanism is connected with carrier (9) of the third planet mechanism and output shaft (11). Epicycle (12) of the third planet mechanism is connected with carrier (13) of the second planet mechanism through clutch (15) and with solar pinion (16) of the first planet mechanism through clutch (14). Solar pinion (16) of the first planet mechanism is connected to brake (17). Solar pinion (20) of the third planet mechanism is connected with brake (19).

EFFECT: reduced sizes and weight.

1 dwg, 1 tbl

 

The invention relates to the transport industry, in particular for vehicles, and can be used in a variety of wheeled and tracked machines.

Known transmission units with speed change gear ratios, containing shafts, bearings, planetary mechanisms and friction controls the Automatic transmission. Charitonov. - M.: OOO "Astrel Publishing house": LLC "Publishing ACT, 2003. - 479, [1] S.: ill.).

These gear units are structurally complex and have large dimensions and weight.

Closest to the proposed kinematic scheme of a transmission (gearbox), selected as a prototype, is synthesized MSTU n.a. Bauman kinematic scheme of the six-speed gearbox (see Automatic transmission. Charitonov. - M.: OOO "Astrel Publishing house": LLC "Publishing ACT, 2003, s-168).

The CP consists of a body placed in it a shaft, three planetary mechanisms, the two coupling clutches and three brakes.

This gearbox has large dimensions and weight, and allows you to implement only one reverse gear. Large overall dimensions and weight are related to the fact that to obtain an acceptable value of gear ratio reverse gear and range are used planetary mechanisms with a large value is an option To, equal to the ratio of the number of teeth of epicycle to the number of teeth of the sun gear, which leads to the use of epitsiklov with a large number of teeth and, consequently, large diameters. In addition, some road construction and tracked vehicles, based on the conditions of work required KP with additional reverse gears or gearbox with full reverse. The application of this gearbox on one of these machines will require the installation of additional reversing mechanism, which, in turn, will lead to the complexity of the design, as well as to increase its dimensions and mass.

The aim of the invention is the reduction of overall dimensions and weight of the gearbox through the use of planetary mechanisms with a smaller value of the parameter K, as well as enhanced operational capabilities and improving the maneuverability of the machine due to the increase in the number of reverse gears.

This objective is achieved in that in the known kinematic diagram containing the input and output shaft, three planetary gear, three brakes and two coupling clutch, apical second planetary mechanism is connected with the planet carrier of the first planetary mechanism, and means coupling the clutch to the input shaft. The second coupling clutch connects the input shaft with a sun gear of the first planetary gear. In the proposed kinematic scheme of one of the coupling IUF which connects the input shaft with the planet carrier of the second planetary gear, and the second was taken with the sun gear of the first planetary gear. This allows, while maintaining range, use the planetary mechanisms with a smaller value of the parameter K, which, ultimately, will lead to reduction of overall dimensions and weight of the gearbox and get an additional reverse gear and, as a consequence, the enhanced operational capabilities and improving the maneuverability of the machine, without increasing the number of planetary gears and controls.

The drawing shows a kinematic diagram of KP.

The table shows the state of the controls on the various programs.

In bearings of the housing 1 is the input shaft 2, which is rigidly connected sun gear 3 of the second planetary gear 4. Apical 5 planetary gear 4 is connected with the planet carrier 6 of the first planetary gear 7, apical 8 which is connected to the planet carrier 9 of the third planetary gear 10 and the output shaft 11. Thus epicycle 12 third mechanism 10 is connected with the planet carrier 13 of the second planetary gear. Coupling coupling 14 connects the input shaft 2 with the planet carrier 13. Coupling sleeve 15 connects the carrier 13 of the second planetary gear 4 with the sun gear 16 of the first planetary gear 7. The brake 17 stops the sun gear 16, the brake 18 - drove 6 planetary gear 7, the brake 19 is a sun gear 20 t is Atego planetary gear 10.

Work KP is as follows.

To obtain the first transmission should be included brakes 18 and 19 (see table). Torque from the input shaft 2 (see drawing) and a sun gear 3 through satellites planetary gear 4 is transmitted to the carrier 13 and epicycle 12. Next torque through satellites planetary gear 10 is transmitted to the carrier 9 and the output shaft 11.

The second gear is engaged brake 17 and 19. Planetary gear mechanism 4 operates in summing mode. On epicycle 5 are added torque: the first is from the input shaft 2 and the sun gear 3, the second from epicycle 12 planetary number 10 and drove 13. From epicycle 5 and led 6 torque through satellites planetary gear 7 is transmitted to apical 8, drove 9 planetary gear 10 and the output shaft 11.

To obtain the third transmission should be included hitch coupler 15 and the brake 19. Planetary gear mechanisms 4 and 7 operate in the summing mode. On epicycle 5 planetary mechanism 4 are summed torque: the first is from the input shaft 2 and the sun gear 3, the second from epicycle 12 planetary gear 10 and the carrier 13. On epicycle 8 planetary series 7 also summarizes torques: the first one is from epicycle 5 and led 6, the second from the sun gear 16 supplied from the carrier 13 of the planetary mechanism 4 through the clutch 15. From epicycle 8 sums the RNA torque is transmitted, as on the previous transfer.

Fourth gear is engaged clutch coupling 14 and the brake 19. Torque from the input shaft 2 and the sun gear 3 through a locked clutch coupling 14 of the planetary gear 4 is transmitted to apical 12. Next torque through satellites planetary gear 10 is transmitted to the carrier 9 and the output shaft 11.

To obtain the fifth (direct) transmission must be enabled coupling of the coupling 14 and 15. Torque from the input shaft 2 through the locked planetary mechanisms is transmitted to the output shaft 11.

The sixth gear is engaged clutch coupling 14 and the brake 17. Torque from the input shaft 2 and the sun gear 3 through the locked clutch 14, the planetary gear 4 is transmitted to the carrier 6. Next torque through satellites planetary gear 7 is transmitted to apical 8, drove 9 planetary gear 10 and the output shaft 11.

The first reverse gear activated clutch coupling 15 and the brake 18. Torque from the input shaft 2 and the sun gear 3 through satellites planetary gear 4 is transmitted to the carrier 13. Further, through the clutch 15, the torque is transmitted to the sun gear 16 and, through satellites planetary gear 7, apical 8, drove 9 planetary gear 10 and the output shaft 11.

To obtain the second reverse gear must be in the turned off coupling sleeve 15 and the brake 17. Torque from the input shaft 2 and the sun gear 3 through satellites planetary gear 4 is transmitted to apical 5 and led 6. Then, through satellites planetary gear 7, the torque is transmitted to apical 8 and then, as on a previous pass.

The economic effect is to reduce size and weight of the gearbox through the use of planetary mechanisms with a smaller value of the parameter K, as well as in enhanced operational capabilities and improving the maneuverability of the vehicle due to an increase in the number of reverse gears.

Transmission, comprising a housing placed in it a shaft, three planetary mechanisms and five friction controls, and a sun gear of the second planetary gear fixed on the input shaft, and epicycle this planetary mechanism is connected with the planet carrier of the first planetary gear and the first brake, and epicycle first planetary mechanism is connected with the planet carrier of the third planetary gear and the output shaft, and apical third planetary mechanism is connected with the planet carrier of the second planetary mechanism, while the sun gear of the first and third planetary mechanisms associated with the second and the third brake, respectively, atricauda is the, what drove the second planetary gear through one coupling clutch is connected with the input shaft, and with the other clutch - with a sun gear of the first planetary mechanism.



 

Same patents:

FIELD: machine engineering, namely powered tools such as drills, screw drivers and rotary cutting tools.

SUBSTANCE: multi-speed transmission unit for rotary powdered tool includes several transmission gears. At least two transmission gears have movable reduction member that provides operation of transmission gears in active and in passive modes. Movable reduction members are joined with mechanism for switching reduction members in order to provide at least three reduction degrees or gear ratio values.

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FIELD: transport engineering.

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