CS218910B1 - Multistage planet gear box - Google Patents

Description

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

Existing planetary gears with five forward gears are based on the Simpson or Wilson kinematic scheme with added gears for the lowest gears. Their disadvantage is the high relative speed of the satellites and the high torques of the internal members at some stages, which places high demands on the satellite bearings and limits the load capacity and service life of the gearbox. Also, the possibility of a more appropriate selection of the size of the gears is made more difficult.

The above drawbacks are overcome by the multi-stage planetary gearbox of the invention, consisting of four single planetary gears, two clutches and four brakes, the essence of which is that the output shaft is rigidly coupled to the second gear ring gear, third gear carrier and central fourth gear. The co-run gear of the first gear is rigidly connected to the carrier of the second gear, with the crown gear of the third gear, and the crown gear of the fourth gear. The forward clutch connects the input shaft to the forward shaft, which is rigidly connected to the sun gear of the third gear. The reverse clutch connects the input shaft to the reverse shaft which is rigidly connected to the sun gear of the first gear and to the sun gear of the second gear. The transmission housing is coupled by a first brake to the reverse shaft, a second brake to the first gear carrier, a third crown brake to the first gear, and a fourth brake to the fourth gear carrier.

Embodiment of the transmission according to the invention is achieved by a lower relative speed of satellites and less stress on the individual gears, thereby ^increase: the durability of bearings and gears.

Fig. 1 is a schematic diagram of a transmission according to the invention.

The output shaft 4 is rigidly connected to the second gear ring gear B, the third gear carrier C and the central gear of the fourth gear D. The crown gear of the first gear A is fixed to the second gear carrier B, the third gear C and the fourth gear D. The forward clutch S1 connects the input shaft 1 to the forward gear shaft 2 which is rigidly connected to the central gear A by means of the third gear C. The reverse clutch S2 connects the input shaft 1 to the reverse shaft 3 which is fixed to the sun gear of the first gear. The transmission housing 3 is connected by the first brake B1 to the reverse shaft 3, the second brake B2 to the carrier of the first gear A, the third brake B3 to the crown wheel of the first gear A and the fourth brake B4 to the carrier of the fourth gear D.

At 1 ° the forward clutch S1 and the fourth brake B4 are engaged. The third gear C and the fourth gear D operate as a compound differential transmission. The first gear A and the second gear B rotate freely without load.

At ΙΓ, the clutch of the forward gear S1 and the third brake B3 are engaged. The third gear C acts as a planetary gear. The first gear A, the second gear B and the fourth gear D rotate freely without load.

At 111 ° the forward clutch S1 and the second brake B2 are engaged. The first gear A, the second gear B and the third gear C operate as a compound differential transmission. The fourth gear D rotates freely without load.

At IV ° the forward clutch S1 and the first brake B1 are engaged. The second gear B and the third gear C operate as a compound differential transmission. The first gear A and the fourth gear D rotate freely without load.

At V ° the forward clutch S1 and the reverse clutch S2 are engaged. The entire planetary part revolves as a whole.

At reverse RI °, reverse clutch S2 and fourth brake B4 are engaged. The second gear B and the fourth gear D work as a compound differential transmission. The first gear A and the third gear C rotate freely without load.

At reverse RII °, reverse clutch S2 and third brake B3 are engaged. The second gear B operates as a simple gear. The first gear A, the third gear C and the fourth gear D rotate freely without load.

At reverse RIII ° the reverse clutch S2 and second brake B2 are engaged. The first gear A and the second gear B work as a compound differential transmission. The third gear C and the fourth gear D rotate freely without load.

The number of operating modes of the transmission according to the invention, as indicated, is maximum and not all achievable gear stages must be used. Thus, for example, RII ° and RIII ° can be omitted.

When using the number of teeth of individual planetary gears

B C D number of ring gear teeth number of sun gear teeth

93,

6, the following gear ratios 1 are obtained for each gear

SI S2 Bl B2 B3 B4 and RIII + + —1.43 RII + -3.44 Rl + —6.17 AND + 3j63 II 4- + 2.63 III ! + + 1.89 IV '+ 1.37 in + + 1.00

SUBJECT V

Claims (1)

Multistage planetary gearbox for motor vehicles and construction machinery, consisting of four single planetary gears, two clutches, and four brakes, where the output shaft is rigidly connected to the third gear carrier and the second gear ring gear, the first gear ring gear is fixed to the second gear carrier - _; with the third gear ring gear, the forward clutch connects the input shaft to the forward gear shaft which is rigidly coupled to the third gear sun gear, the reverse clutch connects the input shaft to the reverse shaft which is rigidly connected to the first gear central gear only a central gear of the second gear, wherein the transmission housing is connected 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 central wheel of the fourth gear (D) is fixedly connected to the output by means of a shaft (4), the fourth gear (D) is fixedly connected to the third gear (CJ) and the gearbox (5) is connected to the fourth gear (D) by means of the fourth brake (B4).