CS215665B1 - Multi-stage planetary gearbox - Google Patents

Abstract

The invention solves the kinematic scheme of a planetary gearbox, consisting of three simple planetary gear sets, two clutches and three brakes. The essence of the invention is the kinematic connection of individual parts of simple planetary gear sets with each other, the placement of two clutches and three brakes. When using three simple planetary gear sets, two clutches and three brakes, four forward and two reverse gears are achieved. Each gear is engaged by engaging one clutch and one brake, or two clutches.

Description

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

Existing gearboxes use a Simpson kinematic scheme with an added planetary gear for the lowest, gear or Wilson. The disadvantage of such wiring is the high, relatively high satellites of the satellites or the high torques on some gears, 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 and ratio is made more difficult.

The above drawbacks are overcome by the multi-stage gearbox of the invention, consisting of three simple planetary gears, two clutches and three brakes, the essence of which is that the output shaft is rigidly connected to the third gear carrier and the second gear ring gear. The ring gear of the first gear is rigidly connected to the carrier of the second gear and to the ring gear of the third gear. The forward seam clutch connects the input shaft to the forward gear shaft, which is rigidly connected to the sun gear of the third gear. A reverse clutch connects the input shaft to a reverse shaft that is rigidly connected to the sun gear of the first gear and the sun gear of the second gear. The transmission housing is connected by a first brake to the reverse shaft, a second brake to the carrier of the first gear, and a third brake to the ring gear of the first gear.

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

Fig. 1 shows one possible circuit diagram of the gearbox according to the invention; Fig. 3 is a schematic diagram of the gears.

The output shaft 4 is rigidly coupled to the third gear carrier Cas by the crown gear of the second gear B. The crown gear of the first gear A is rigidly coupled to the driver of the second gear B and the crown gear of the third gear C. which is fixedly connected with the sun gear around the third clutch C Reversing S2 connects the input shaft 1 to the shaft 2 · reverse reverse shaft 3 is fixedly connected with the sun gear of the first gear set and the sun gear and the second gear B. the gearbox housing 2 coupled first ^e J the brake B1 with the reverse shaft 3, the second brake B2 with the carrier of the first gear A and the third brake B3 β crown wheel of the first gear A.

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

At 11 ° the forward clutch S1 and the second brake B2 are engaged. The first gear A, the second gear B and the third gear C constitute a compound differential transmission.

At 111 ° the forward clutch S1 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 reverse clutch S2 are engaged at the same time. The entire planetary part revolves as one.

At reverse R1, reverse clutch S2 and third brake, B3, are engaged. The second gear B operates as a simple gearing, the first gear A and the third gear C rotate freely without load.

At reverse RII ° the reverse 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 gear set C rotates freely without load.

When choosing planetary gear teeth:

gearing:

number of cog wheel teeth: 85 number of cog wheel teeth: 27?

the following gears are achieved for each gear:

BII Rl I II III IV -1.43 -3.44 2.63 1.89 1.37 1.00

Figure 3 shows the maximum number of operating modes. Some operating modes and corresponding gear ratios may not be used, such as reverse BII.

Claims (1)

SUBJECT OF THE INVENTION Multistage planetary gearbox for motor vehicles and construction machinery, consisting of three simple planetary gears, two clutches and three brakes, characterized in that the output shaft (4) is rigidly connected to the gripper of the third gear (C) and the crown wheel of the second gear (B), the first gear ring (A) is rigidly connected to the second gear carrier (B) and the third gear ring (C), the forward clutch (Sl) connects the input shaft (1) to the forward gear shaft (2), which is firmly connected with the third gear (C), the reverse clutch (S2) connects the input shaft (1) to the reverse shaft (3), which is rigidly connected to the first gear (A) and second gear (B), the housing the transmission (5) is connected by the first brake (B1) to the reverse shaft (3), the second brake (B2) to the grip of the first gear (A) and the third brake (B35 with the crown wheel) the first gear (A).