CS212848B1 - Multistage epicyclic gear - Google Patents

Abstract

The invention solves the kinematic scheme of the planet gearboxes made up of three simple ones gears, three clutches and three brakes. The subject of the invention is a kinematic bond of single planetary parts gears among themselves, placed three clutches and three brakes. When using three simple ones planetary gears, three clutches and three brakes are achieved by six forward and a two reverse gears. Each the gearbox is engaged by switching one clutch and one brake, or two clutches. Figure 1 best describes the subject matter invention.

Description

The subject of the invention is a multi-stage planetary gearbox for motor vehicles and construction machines, consisting of three simple planetary gears, three clutches and three brakes.

Existing gearboxes use a Simpson kinematic diagram with an added planetary gear for the lowest gear or Wilson. The disadvantage of these connections is the high relative speed of the satellites, or the high torques on some gear transmissions, which places high demands on the satellite bearings and limits the load capacity and service life of the gearbox. Also, the possibility of choosing a more suitable gear ratio is more difficult.

The above drawbacks are overcome by the multi-stage planetary gearbox according to the invention, consisting of three simple planetary gears, three clutches and three brakes, characterized in that the overdrive clutch connects the input shaft β to the overdrive shaft which is rigidly connected to the second gear carrier.

The gearbox according to the invention achieves a lower relative speed of the satellites and reduces the load on the individual planetary gears, thereby increasing the life of the bearings and the gearing.

Fig. 1 shows one possible schematic circuit diagram of the gearbox according to the invention;

another variant of the schematic connection is shown and in FIG.

The output shaft is rigidly connected to the carrier of the third gear C and the ring gear of the second gear B. The carrier of the second gear B is. rigidly coupled to the crown wheel of the first gear A and to the crown wheel of the third gear C. The forward clutch S1 connects the input shaft 1 to the forward gear shaft 2 which is rigidly connected to the sun gear of the third gear C. 3, which is rigidly connected to the second gear carrier Bas by the crown wheels of the first gear A and the third gear C. The reverse clutch S3 connects the input shaft 1 to the reverse shaft 4, which is rigidly connected to the sun gear of the first gear A and the sun gear of the second gear B.

The transmission housing 6 is connected by a first brake B1 to a reverse shaft 4, a second brake B2 to a carrier of the first gear A and a third brake Bg to a crown wheel of the first gear A.

At 1 ° the forward clutch S1 and the third brake B3 are engaged. The third gear C works as a simple planetary gear. The first gear A and the second gear B rotate freely without load.

At 11 ° the forward clutch S1 and the second brake B2 are engaged. All three gears A ,. B and C are loaded and operate as a compound differential transmission.

At 111 ° the forward clutch A1 and the first brake B1 are engaged. The second gearing B and the third gearing C operate as a compound differential transmission, the first gearing A rotating freely without load.

At IV ° the forward clutch S1 and the overdrive clutch S2 are engaged. The entire planetary part revolves as one.

At V ° the overdrive clutch S2 is engaged. The second gear B works as a simple planetary gear. The first gear A and the third gear C rotate freely without load.

At VI ° the overdrive clutch S2 and the second brake B2 are engaged. The first gear A and the second gear B work as a compound differential transmission. The third gear C rotates freely without load

212 848

At reverse RII °, reverse clutch S3 and second brake B2 are engaged. The first gear A and the second gear B act as a compound differential transmission. The third gear C rotates freely without load.

When choosing planetary gear teeth:

gears number of ring gear teeth the number of teeth of the sun gear is achieved by the individual gears

RII RI II

-1.43 -3.44 2.63 1.89

AND (B) C 85 93 93 27 Mar: 27 Mar: 57 gears: III IV IN VI 1.37 1.00 0.77 0.45

Number of operating modes ximal. Some of the achievable transmissions of the present invention, as shown in Fig. 3, is the gear ratio may not be utilized, for example VI and RII.

Claims (1)

Multistage planetary gearbox for motor vehicles and construction machinery, consisting of three simple planetary gears, three clutches and three brakes, where the output shaft is rigidly coupled to the third gear carrier and the second gear ring gear, the second gear carrier is rigidly connected to the first gear ring gear with the third gear ring gear, the forward clutch connects the input shaft to the forward gear shaft that is rigidly coupled to the third gear sun gear, the reverse clutch connects the input shaft to the reverse shaft that is rigidly coupled to the first gear sun gear and the second gear sun gear the transmission housing being coupled by a first brake to the reverse shaft, a second brake to the first gear carrier, and a third brake to the first gear ring gear, characterized in that the ryohlobshh clutch (S2) connects the input shaft (1) to the ryohlobshha shaft (3), which is firmly connected to the β carrier of the second gear (B).