CS219393B1 - Multistage planet gear box - Google Patents

Abstract

The invention solves the kinematic scheme of the planet gearbox, consisting of four simple ones planetary gears, two clutches and four brakes. The subject of the invention is a kinematic bond of single planetary parts gears between themselves, the location of the two clutches and four brakes, when using four simple planetary gears, two clutches and four brakes are achieved by five forward and a two reverse gears. Each the gear is engaged by one clutch and one brake, or two clutches.

Description

The invention solves a kinematic diagram of a planetary gearbox consisting of four simple planetary gears, two clutches and four brakes.

The invention is based on the kinematic coupling of the individual parts of the single planetary gears with one another, the placement of two clutches and four brakes. Each gear is engaged by engaging one clutch and one brake or two clutches.

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.

The disadvantages of existing planetary five-speed gearboxes, largely based on the Wilson or Simpson kinematic scheme, are the high relative speed of the satellites and the high torques at some stages, which increases the bearing capacity of the satellite bearings and limits the life and load capacity of the transmission. Also, the ability to choose a finer gear ratio is difficult and requires the selection of disadvantageous gear wheel dimensions.

The above-mentioned drawbacks are eliminated by the multi-stage planetary gearbox according to the invention, consisting of four simple planetary gears, two clutches and four brakes, the principle being that the fourth gear carrier is fixedly connected to the output shaft and third gear ring gear. with the reverse shaft, and the transmission housing is coupled with the fourth brake to the fourth gear ring gear.

The design of the transmission according to the invention results in a lower relative speed of the satellites, lower torques and a more suitable gear ratio, which contributes to a longer service life and load capacity of the transmission. It is also possible to select suitably the same number of teeth for all four simple planetary gears in order to increase the construction technology.

Fig. 1 is an example of a schematic circuit of the gearbox according to the invention; Fig. 2 is a shifting diagram.

The output shaft 4 is rigidly coupled to the first gear carrier A, the third gear ring C and the fourth gear carrier D. The second gear B gear is rigidly connected to the third gear carrier C. The forward gear clutch SI connects the input shaft 1 to the forward gear shaft The reverse clutch S2 connects the input shaft 1 to the reverse shaft 3, which is rigidly connected to the sun gear of the first gear A, the sun gear of the second gear B, the sun gear of the third gear C and s. the gearbox 5 is connected by the first brake B1 to the reverse shaft 3, the second brake B2 to the carrier of the second gear B, the third brake B3 to the crown wheel of the second gear B and the fourth brake B4 to the crown wheel of the fourth gear D.

At 1 ° the reverse clutch S2 and fourth brake B4 are engaged. The fourth gear D works as a simple planetary gear. The first gear A, the second gear B and the third gear C rotate freely without load.

At ΙΓ the forward clutch S1 and the third brake B3 are engaged. The first gear A and the third gear C work as a compound differential transmission. The second gear B and the fourth gear D rotate freely without load.

In IIP, the forward clutch S1 and the second brake B2 are engaged. The first gear A, the second gear B and the third gear C are referred to 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 first gear A operates as a simple planetary gear. The second gear B, the third gear C 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 R1 °, reverse clutch S2 and third brake B3 are engaged. The third gear C operates as a simple gear. The first gear A, the second gear B and the fourth gear D rotate freely without load.

At reverse RII ° the reverse clutch S2 and the second brake B2 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.

When choosing planetary gear teeth:

number of teeth of crown wheel 77 number of teeth of sun wheel 25

77 77

25 25 the following gears are achieved for each gear:

RII RI I II III IV V —1.33 —3.08 4.08 2.33 1.76 1.33 1.00

The number of gears of the transmission according to the invention, as shown in FIG. 2, is maximum. Some available operating modes may not be used, such as RII ° return.

Claims (1)

SUBJECT Multistage planetary gearbox for motor vehicles and construction machines, consisting of four simple planetary gears, two clutches and four brakes, where the output shaft is fixedly connected to the carrier of the first gear, the second gear is fixed to the third gear carrier, the forward clutch connects the input a forward gear shaft that is rigidly coupled to the first gear ring gear, a reverse clutch connects the input shaft with a reverse gear shaft that is rigidly coupled to the central gear of the second gear, with the sun gear of the third gear, the transmission housing coupled to the first brake a reverse gear shaft, a second brake with a second gear carrier and a third crown wheel brake of the second gear, characterized in that the fourth gear carrier (D) is rigidly connected to the output shaft (4) and the third gear (C), c the input gear · of the fourth gear (D) is fixedly connected to the reverse shaft (3) and the gearbox housing (5) is connected to the fourth gear (Dj.