RU2021910C1 - Gearbox - Google Patents

Abstract

FIELD: automobile vehicles: trucks, tractors, road-building and agricultural machinery. SUBSTANCE: operation of external gears is intensified owing to their free fitting on coaxial shafts and introduction of additional shaft with rigidly secured gear, introduction of planetary mechanism and installation of all control sleeves on coaxial shafts. EFFECT: enhanced reliability of operation. 2 dwg, 2 tbl

Description

 The invention relates to transport engineering, to the transmission of transport vehicles.

 Known transmission units with step change of gear ratios, containing gears, shafts, bearings, gearshift devices used on domestic and foreign cars (automobiles: design, construction and calculation. Transmission / Edited by A.I. Grishkevich. - Mn .: High school 1985 .-- 240 s.).

 These units are structurally complex, metal-intensive.

 Closest to the proposed gearbox (KP) is an eleven-speed gearbox, which consists of a housing with shafts located in it, a single-row three-link simple planetary gear, six external gears and five control couplings.

 Such a CP has limited kinematic capabilities.

 The purpose of the invention is the expansion of the kinematic capabilities of the KP by increasing the number of gears and range.

 This goal is achieved by the fact that on the intermediate shaft all the gears are mounted rigidly, between the input shaft and the shaft of the sun gear drive, there is a pinion shaft engaged with the middle gear of the intermediate shaft, between the pinion shaft and pinion freely mounted on the carrier shaft of the carrier, two three-position couplings are placed.

 The expansion of kinematic capabilities was achieved due to the intensification of the use of external gears, which at the entrance to the planetary mechanism (PM) provide four gears instead of three, as well as PM due to the installation of all control couplings on coaxial shafts.

 Figure 1 shows a diagram of the gearbox with 18 steps of forward and 4 - reverse; figure 2 is a beam diagram of the KP.

 In the table. 1 shows the operation of switching clutches - connecting parts at different positions of the couplings; Table 2 shows the positions of the control couplings in various gears.

 Shafts 2 and 3 and an output shaft 4 are installed coaxially with the input shaft 1. On the shaft 3 is a tubular shaft 5. Parallel to the shafts 1-3, an intermediate shaft 6 is installed with gears 7-9 rigidly fixed thereon. Gear 9 is engaged with gear 10 freely mounted on shaft 1. Gear 2 is fixed on shaft 2 and engaged with gear 8. Gear 12, freely mounted on tubular shaft 5, is engaged with gear 7. Sun gear (a) 13 of the planetary gear (PM ) mounted on the shaft 3. On the tubular shaft 5 the carrier h 14 is fixed with satellites 15 engaged with the sun gear 13 and the epicyclic gear b 16 PM. Five control couplings are located on the coaxial shafts: A, B, C, D, E.

 The work of the CP is as follows.

 PM implements six reduction gears and two differential (summing) gears.

 One variant of differential transmission occurs when torque is applied to the sun gear a and to the carrier h, and the torque output from the epicyclic gear b. So 1 and 2 transfers are realized (figure 2). The second variant of differential transmission occurs when torque is applied to the solar and epicyclic gears, and the torque output from the carrier. So 11 and 13 transfers are realized (figure 2).

The slowest transmission in the PM is formed when the epicyclic wheel b is stopped - U _ah ^b , where the upper index indicates the stopped link, and the lower indices indicate the entrance and exit of the PM. The moment enters the PM on the sun gear a, and the increased moment is removed from the carrier h. Thus, four gearboxes are implemented in the gearbox: 3, 4, 7, and 9. The gear ratio at the input to the PM changes due to external gears.

Slow gear in PM - U _bh ^a occurs when the sun wheel ^a is stopped. Torque is applied to the epicyclic wheel b, the increased moment is also removed from the carrier h. Thus, two transfers are implemented - 5 and 6.

 Direct transmission to the PM is formed when it is blocked — a rigid connection of any two links — or when the moment is transmitted through one of the PM links. Thus, four transfers are realized: 8, 10, 15 and 17.

An accelerating gear in PM is also formed when the sun gear is stopped - U _hb ^a , as with a slow gear, but the input and output of the moment have changed. The moment enters the carrier h, a reduced moment, but with an increased speed, it is removed from the epicyclic gear b. Thus, two gears are implemented: 12 and 14.

The maximum increase in the rotational speed at the exit of the PM with respect to its input occurs when the epicyclic wheel is stopped - U _ha ^b , the moment, as in the previous case, enters the carrier h, and is removed from the sun gear a. Thus, two transfers are realized: 16 and 18.

Reverse gears - U _ab ^h are formed when the carrier h is stopped, the moment is input to the sun wheel a, and the output is from the epicyclic wheel b. Thus, all four reverse gears are realized.

1st gear
From the input shaft 1, the torque through the clutch A in the first position, the gears 10 and 9 enters the intermediate shaft 6, where it branches into two streams. The first stream - from the shaft 6 through gears 7 and 12, the coupling C in the third position enters through the tubular shaft 5 to the carrier h 14, the second stream - from the shaft 6 through the gears 8 and 11, along the shaft 2, through the coupling B in the third position on the shaft 3 and the sun gear a 13. Both flows are summed up on the epicyclic gear b 16 and through the clutch E in the first position enter the output shaft 4. The clutch D is in the third (neutral) position.

 The gears are shown in the radiation diagram. The vertical beam corresponds to a transmission with U = 1.0; the beam directed to the right corresponds to a deceleration gear, to the left - to an accelerating gear.

 In the first gear (FIG. 2), the total momentum stream is reflected by a ray 10-9, the first stream - by a ray 7-12 and its gentle extension to point 1, the second stream - by a beam 8-11 and a gentle beam also to point 1.

2nd gear
Differs from the first transmission by the power flow input. Clutch A in the third position connects the input shaft 1 to the shaft 2 and gear 11.

3rd gear
The entrance to the PM corresponds to the first stream of the first transmission (figure 2 and table. 2). Torque is supplied to the sun wheel and through the clutch C in the first position (Table 1), the increased moment is removed from the carrier h through the clutch E in the second position. Epicyclic wheel b is stopped by clutch D in the fourth position.

4th gear
The entrance to the PM corresponds to the first stream of the second gear, the work of the PM corresponds to the third gear (figure 2 and table 2). Differs from third gear by switching clutch A to third position.

5th gear
The entrance to the PM corresponds to the 1st and 3rd gears, the sun wheel a is fixed relative to the gearbox housing by clutch B in the second position. Torque is applied to the epicyclic wheel b through the coupling D in the first position (Fig. 2, tables 1 and 2). The increased moment is removed through the clutch E in the second position.

6th gear
The entrance to the PM corresponds to the 2nd and 4th gears, the PM to the 5th gear. Differs from fifth gear by switching clutch B to third position.

7th gear
Torque comes from shaft 1 through clutch A in the first position, gears 10 and 9, shaft 6, gears 8 and 11, through clutch B in third position and further, as in 3rd and 4th gears.

8th gear
Corresponds to the 3rd gear, but couplings C and D are in the third position (Table 2).

9th gear
Corresponds to 7th gear, but clutch A is in third position.

10th gear
Corresponds to the 8th gear, but clutch A is in the third position.

11th gear
It corresponds to the first gear, but instead of the carrier, one of the moment flows flows to the epicyclic wheel b from gear 12 through the coupling D in the first position, the flow exits through the coupling E in the second position from carrier h to the shaft 4. The coupling C is in the second (neutral) position.

12th gear
The entrance to the PM corresponds to 1st, 3rd, 5th and 8th gears. The sun gear a is stopped relative to the gearbox housing by the clutch B in the second position, the moment enters the carrier h from the gear 12 by the clutch C in the third position, the moment is removed from the epicyclic wheel b by the clutch E in the first position. Clutch D in the third (neutral) position (table 2 and figure 2).

13th gear
The state of the planetary gear corresponds to the 11th gear, but clutch A is in the third position.

14th gear
Corresponds to 12th gear, but clutch A is in third position.

15th gear
The moment from the shaft 1 through the clutch A in the first position is transmitted by the gears 10 and 9, then along the shaft 6, the gears 8 and 11, through the clutch B in the third position, goes to the shaft 3 and is removed from it by the clutch E in the third position. Clutch D in the third (neutral) position (figure 2 and table.).

16th gear
Before PM, the moment arrives, as in gears 1, 3, 5, 8 and 12, but the moment from gear 12 is transmitted to carrier h through clutch C in the third position, the epicyclic wheel b is stopped by clutch D in the fourth position, the moment is removed from the sun gear a coupling E in the third position. Clutch B in the first (neutral) position.

17th gear - direct
The coupling A in the third position connects the shafts 1 and 2, the coupling B also in the third position connects the shafts 2 and 3, the coupling E also in the third position connects the shafts 3 and 4. The coupling C in the second (neutral) position.

18th gear
Corresponds to 16th gear, but clutch A is in third position.

 Reverse gear.

1st gear
Before PM, the moment arrives, as in gears 1, 3, 5, 8, 12, and 16. Like in third gear, the moment enters the sun gear through clutch C in the first position, but the moment is removed from the epicyclic wheel through clutch E in the first position, when the carrier is stopped, fixed relative to the gearbox housing by clutch D in the second position.

2nd gear
Differs from the first by switching clutch A from the first position to the third.

3rd gear
It differs from the first gear by switching the clutch B into the third, and the clutch C into the second position.

4th gear
Differs from the third by switching clutch A to the third position.

 If the internal parameter of the planetary mechanism K = Zb / Za and the gear ratios of the pairs of gears of the external gearing change, the nature of the gearbox distribution will change.

 The economic effect is expressed in the expansion of the kinematic capabilities of the gearbox - the number of forward gears increased from 11 to 18, the number of reverse gears doubled, while the range of the gearbox was expanded by increasing the gear ratio of the lower gear to 17. The expansion of the kinematic capabilities of the gearbox allows the vehicle to be operated at the optimum economic and environmental regime with minimum fuel consumption and the emission of harmful substances from engine exhaust gases.

Claims (1)

 GEARBOX containing a housing with shafts, external gears, a single-row planetary gear, control clutches, all shafts, except the intermediate one, are mounted coaxially, a coupling is installed on the output shaft, through which the shaft is connected to one of the links of the planetary gear, tubular the carrier drive shaft is located on the drive shaft of the sun gear of the planetary mechanism, three gears of external gearing are installed on the intermediate shaft, characterized in that the entire shaft is on the intermediate shaft IDH mounted rigidly between the input and output shaft and the drive shaft of the sun gear has an additional shaft fixedly mounted thereon a pinion meshed with the middle gear wheel of the intermediate shaft between the additional shaft and pinion freely mounted on the tubular drive shaft of the carrier, two three-position clutches arranged.

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