CS264062B1 - Multi-stage planetary gear with fine / c gradation of gears - Google Patents

Abstract

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

Description

The subject of the invention is a multi-stage planetary gearbox with fine gear ratios for motor vehicles and construction machinery, consisting of three input clutches, four brakes and four simple planetary gear sets.

Most known fine-pitch planetary gearboxes consist of two input clutches, four brakes and four simple planetary gears, in which the output shaft is connected only to the carrier of the fourth planetary gear in a so-called differential connection. These gearboxes provide five forward and three reverse gears, and shifting between any adjacent gears is carried out by turning off only one and turning on only one clutch or brake. If it is necessary to increase the gear range and the number of gears, this requires the connection of another planetary gear, brake and clutch, which is disadvantageous in terms of space and manufacturing requirements.

The above-mentioned shortcomings are eliminated by the multi-stage planetary gearbox according to the invention, the essence of which is the addition of a third input clutch, which, through the high-speed shaft, can firmly connect the input shaft with the carrier of the second planetary gear set. This achieves three more forward stages without a significant increase in the installation dimensions and complexity of the gearbox.

Figure 1 shows an example of a kinematic diagram of a transmission according to the invention.

The output shaft 5 is rigidly connected to the carrier of the fourth gear set L>. The forward clutch 31 connects the input shaft to the forward shaft 2, which is rigidly connected to the crown gear.

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264 062 around the second gear B, with the sun gear of the third gear C and the sun gear of the fourth gear D. The overdrive clutch S 2 connects the overdrive shaft 3 with the input shaft JL« The overdrive shaft 3 is firmly connected to the carrier J7 of the second gear B, the carrier of the third gear C and the crown wheel of the fourth gear D. The reverse clutch S3 connects the input shaft JL with the reverse shaft 4, which is firmly connected to the sun gear of the first gear A and the sun gear of the second gear 3. The crown wheel of the first gear A is firmly connected to the crown wheel of the third gear C and the third brake 33 is connectable to the gearbox chamber 6. The gearbox housing C> is further connectable by the first brake B1 with the reverse shaft 4, the second brake 32 with the carrier of the first gear A and the fourth brake with with the crown wheel of the fourth gear set D, and thus also with the shaft of the overdrive 3.»

At 1°, the clutch of forward gears 31 and the fourth in

brake B1. The fourth gear set n works as a single planetary gear. The other gears A, B, and C rotate freely without backlash. £3

At II, the forward clutch S1 and the third brake are engaged. The third gear set C and the fourth gear set B operate as a compound planetary gear with a differential at the output. The first gear set A and the second gear set 3 rotate freely without load.!· o * <*

At speed III, the forward clutch SJL and the second brake B2 are engaged. All four planetary gears A, B, C and D form a compound planetary transmission with a differential at the output.

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At IV° the brake Bl. The second n v t o v y m s c ha *;i m and the third gear set engage the clutch of the forward gears oJ, and the first gear set B and the fourth gear set B t»jří compound :„us with the differential at the output. Brve gear set ·

G are free to rotate bon load.

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At V°, the forward clutch 51 and the reverse clutch S3 are engaged and the planetary part rotates as one unit with a gear ratio of 1.0»

At VI°, the overrunning clutch S2 is engaged. and the first brake Bl ♦ The second gear B and the fourth gear D form a compound planetary gear. The first gear A and the third gear C rotate freely without load.

At VII°, the overdrive clutch 52 and the second brake Bj are engaged. All four gear sets Λ, B, C and D form a composite planetary mechanism with a differential at the output.

At VIII ^0, the overrunning clutch 52 and the third brake B1 are engaged. The third gear set C and the fourth gear set D form a compound planetary gear. The first gear set A and the second gear set B rotate freely without load.

In reverse gear ΠΙ°, the reverse clutch 33 is engaged and the fourth brake Bl. Bruk/ gear set 2 operates as a simple gear, the fourth gear set D operates as a planetary gear. The first gear set A and the third gear set C rotate freely without load.

In reverse gear EII°, reverse clutch 53 and third brake B3 are engaged. Gear sets 3, C, and D form a compound planetary gear. First gear set A rotates freely without load.

In reverse gear EIII°, the reverse clutch 53 and the second brake B2 are engaged. All gear sets A, E, C and D form a compound planetary gear.

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The sorting scheme is clearly shown in the table:

SI S2 33 Bl B2 B3 B4 To III + + i < 0 if II + + R I + . + I + 4· i > 1 II 4* ·{· III + + IV + 4- .in + i- 1 = 1 VI + C < i < 1 Ί x X •i- + νγτ r ť Λ x x -r +

SUBJECT OF THE INVENTION

Claims (1)

OBJECT OF THE INVENTION 264 062 Multistage planetary gearbox with fine gearing for motor vehicles and construction machinery, consisting of four simple planetary gears, forward clutch, reverse clutch and four brakes, where the second planetary gear carrier is rigidly connected to the third planet gear carrier and the fourth planetary gear ring, the ring gear of the first planetary gear is fixed to the ring gear of the third planetary gear, the sun gear of the first planetary gear is fixed to the sun gear of the expensive planetary gear, the ring gear of the second planetary gear is tightly connected to the sun gear of the third planetary gear , the spindle is firmly connected to the carrier of the fourth planetary gear, the reverse clutch is the input shaft connectable to the reverse shaft and further to the central around the first planet gear, the gear ratio is input, the gear is connected to the forward gear, and the ring gear of the second planet gear, the gearbox is connectable with a first brake with a reverse shaft, a second brake with a carrier of the first planetary gear a fourth planetary gear set and a fourth ring gear, characterized in that the input shaft (1) is an overdrive clutch (S2) connectable to the overdrive shaft (3) fixedly coupled to the carrier (7) of the second planetary gear set (B);