CS220383B1 - Multispeed epicyclic gearbox - 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, placing two clutches and four brakes, when using four simple planetary gears, two clutches and four brakes are reached five forward and two reverse gears. Each The gear is engaged 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.

Existing planetary gearboxes are based on the Simpson or Wilson kinematic diagram with the added gears for the lowest gear. The disadvantages of these gearboxes are the high relative speed of the satellites and the high load moments on some gears, which places high demands on the satellite bearings and limits the load capacity and service life of the gearbox. Also, a more appropriate choice of gear ratio is more difficult.

The above-mentioned 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 fourth gear carrier is rigidly connected to the output shaft and the third gear ring gear. The sun gear of the fourth gear is rigidly connected to the forward gear shaft and the gearbox housing is connected to the fourth gear ring gear by the fourth brake.

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

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

The output shaft 4 is rigidly connected to the ring gear of the second gear B, with the carrier of the third gear C and with the carrier of the fourth gear D. The crown gear of the first gear A is firmly connected with the carrier of the second gear B. 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 transmission housing 5 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 crown around the fourth gear D.

At 1 ° the forward clutch S1 and the 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 11 ° the forward clutch S1 and the third brake B3 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 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 øV ° the forward clutch S1 and the first brake B1 are engaged. The third gear C works as a simple planetary gear. The first gear A, the second gear B 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 spins as one.

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

When reverse gear RIP, reverse clutch S2 and third brake B3 are engaged. 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.

B C D Number of ring gear teeth 77 77 77 77 Number of sun gear teeth 25 25 25 25 The following gears are achieved for each gear:

RII RI I II III IV V - 3.08 - 8.49 4.08

The number of operating modes of the transmission according to the invention as shown in FIG. 2 is maximum. Some of the achievable gears 2, .313, 1.73, 1.33, and 1.00 degrees may not be utilized, for example, the return RII °.

SUBJECT

Multistage planetary gearbox for motor vehicles and construction machinery, consisting of four simple planetary gears, two clutches and four brakes, where the second gear ring gear is rigidly connected to the third gear carrier, the first gear ring gear is rigidly connected to the second gear carrier. the forward clutch connects the input shaft to the forward shaft which is rigidly coupled to the third gear ring gear, the reverse clutch connects the input shaft to the reverse shaft that is rigidly coupled to the first gear central gear to the central gear

Claims (1)

OF THE INVENTION around the second gear and the sun gear of the third gear, wherein the transmission housing is connected by a first brake to the reverse shaft, a second brake to a first gear carrier, a third crown wheel braking of the first gear, characterized in that the fourth gear carrier the output shaft (4) and the third gear ring gear (C), the fourth gear (DJ is fixed to the forward gear shaft (2) and the gearbox (5) is connected to the fourth gear (DJ) by the fourth brake (B4) .