RU2053140C1 - Transfer case - Google Patents

Abstract

FIELD: transport engineering. SUBSTANCE: number of speeds is increased owing to freely fitting the gears on shafts. Planetary mechanism increases number of speeds and range of transmission gear ratios and provides reverse owing to operation under summing up duty when torque is transmitted to sun gear 15 and carrier 13 and is removed from epicyclic wheel 16. EFFECT: enlarged operating capabilities. 3 dwg

Description

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

 Known transfer case (RK), consisting of a speed gearbox (KP), combined with an interaxle differential, containing gears, shafts, their bearings, gear shifting devices used on domestic and foreign cars (Osepchugov V.V. Frumkin A.K. Automobile: Structural Analysis, Elements of Calculation. M. Mechanical Engineering, 1989, p. 304).

 These transmission units are metal-intensive, have limited kinematic capabilities.

 Closest to the proposed is the RK of the KAZ-4540, consisting of an 8-speed gearbox combined with a single-stage differential gearbox containing 16 gears (13 in the gearbox and 3 in the gearbox), 4 shift clutches, a differential and a differential lock clutch (ibid., fig. 40 and 50, p. 63 and 74).

 Such a RC has a high metal consumption with limited kinematic capabilities, since 16 gears are required to separate the power flow in 8 gears.

 The aim of the invention is to expand the kinematic capabilities of the unit while reducing its metal consumption.

 The goal is achieved by the fact that three separate gears are freely mounted on the input shaft, and the planetary sun gear is fixed to the shaft output, a tubular drive shaft of this mechanism is located between them, a fourth gear is freely installed on the tubular shaft, all freely installed gears are engaged with gears, coupled in two blocks and freely mounted on the intermediate shaft, a clutch is located between the gear blocks, interconnected with a similar clutch located between the middle gears by the input shaft, two couplings are installed on the hubs located between the separate gears on the primary and tubular shafts, the differential carrier shaft is located coaxially with the primary shaft, the outputs of the sun gear and the epicyclic planetary gear wheel are located on it, and a hub with a coupling is fixed, one of the differential gears are mounted on an output shaft mounted coaxially with the input shaft, the other differential gear is connected by a tubular shaft to the gear on which the differential lock clutch is located erentsiala, this gear is engaged with a pinion fixed to the countershaft.

 Figure 1 shows a diagram of a transfer case having 13 forward gears and 2 reverse gears.

 Figure 2 shows the radiation diagram of this RK. The vertical beam corresponds to a gear ratio of 1.0. A beam directed to the right indicates a deceleration gear, the better the beam, the greater the gear ratio of a pair of gears or gears. A beam pointing to the left indicates an accelerating gear.

 Figure 3 shows the position of the couplings in various gears.

 In the bearings of the housing 1 there is a primary shaft 2, on which gears 3-6 are freely mounted, engaged with gears 7-10, also freely mounted on the intermediate shaft 11. Gears 7-8 and 9-10 are combined into blocks. At the output of the primary shaft 2 is a tubular shaft 12 of the drive carrier 13 of the planetary gear. The satellites 14 mounted on the carrier 13 are engaged with the sun gear 15, mounted on the input shaft 2, and with the epicyclic wheel 16. The carrier 13 and the epicyclic wheel 16 are supported on the shaft 17, which is aligned with the primary shaft 2. The differential carrier 18 is mounted on the shaft 17 which the gears 19 are engaged with the gear 20 fixed on the output shaft 22, coaxial to the shafts 2 and 17. The satellites 19 are also engaged with the differential gear 20, which is connected by a tubular shaft to the gear 23 engaged with the gear 24 mounted on the intermediate shaft eleven.

 Clutch A is placed between gears 3 and 4 on the hub of the input shaft 2, interconnected couplings B are located on both shafts between the middle gears 4-5 and 8-9, clutch C is installed on the hub of the tubular shaft 12 between gears 5 and 6. Clutch D of the planetary gear mounted on the hub of the shaft 17 between the planetary gear and the differential, the differential lock clutch E is located on the gear 23.

 The work of the Republic of Kazakhstan is as follows.

 The planetary gear at the output of the gearbox operates in two modes. The first mode (torque) is applied to the two links of the sun gear 15 and the carrier 13, satellites 14 both flows are summed up on the epicyclic wheel 16 and removed from it by the differential clutch D. Thus, reverse gears are obtained, forward gears 1, 2, 7, 8 and 13. Other transmissions are formed when the moment is transmitted directly through the planetary mechanism via carrier 13 and clutch D to the differential.

 Transmission 1. Clutches A and C in the right position (figure 3), and the clutch B and D in the left position.

 From the input shaft 2 (Fig. 1) to the epicyclic wheel 16, the torque is supplied in two ways. The first path goes directly to sun gear 15 and satellites 14. The second path goes through clutch A, gear 4, clutch B, a pair of gears 5-9, a block of gears 9-10, a pair of gears 10-6, a clutch C, a shaft 12 on carrier 13 and satellites 14. Satellites 14 both flows are summed up on the epicyclic wheel 16, the clutch D and the shaft 17 are transmitted to the carrier 18 of the differential. The differential gears 19 divide the torque in proportion to the radii of the gears 20 and 21. From the gear 21 by the shaft 22, part of the moment is transmitted by cardan transmission to the rear bogie of the drive axles, if the differential is asymmetric, as in FIG. 1, or on one bridge if the differential is symmetrical. An asymmetric differential can also be used to drive one rear axle if the drive axles are unevenly loaded, such as a timber truck. From gear 20, another part of the moment is transmitted by a tubular shaft to gears 23 and 24, then along shaft 11 to the cardan drive of the front drive axle drive.

 In the radiation diagram (figure 2) this transmission is represented by two streams of rays. The first stream from point O is directed vertically down to the second horizontal; for this stream, point O is conventionally moved to this horizontal, then a gentle beam 2-15-14 is directed down to the right to point 1 on the axis of the gear ratio logarithm. On the lowest horizontal, this gear will correspond to a gear ratio> 20. The second stream also from point O consists of rays: 5-9 steeply down to the right, then in the same direction a more gentle beam 10-6 and the last beam 12-13-14, the most gentle to point 1.

 Transmission 2. Switch the clutch in the right position (figure 3).

 The moment is also transmitted in two streams. This transmission differs from the previous one only by replacing a pair of gears 5-9 with a pair of gears 4-8 (Fig. 1).

 In the beam diagram (figure 2), compared with the previous transmission, the rays have shifted to the left, the place of the beam 5-9 is occupied by a vertical beam 4-8. A slight change in the difference in the rotation speeds of the sun gear 15 and the carrier 13 0.08 on the middle axis of the gear ratio logarithm, significantly accelerated the rotation speed of the epicyclic wheel 16 0.52 on the lower axis of the gear ratio logarithm.

 Transmission 3. Switch the clutch A and B in the left position, and the clutch D in the right position (figure 3).

 The moment is transmitted in a single stream. From the input shaft 2 by coupling A to a pair of gears 3-7, then along block 7-8, a pair of gears 8-4, coupling B, a pair of gears 5-9, a block 9-10, a pair of gears 10-6, a coupling C, a shaft 12, drove 13 to the clutch D and then, as in previous gears (figure 1).

 In the radiation diagram (figure 2), this transmission is represented by five rays: beam 3-7 from point O down to the right, 8-4 vertically down, 5-9 right up, 10-6 gently sloping right down and the last beam connecting shaft 13-17 vertically down to point 3 on the axis of the logarithm of the gear ratio.

 Transmission 4. Switch the clutch In to the right position (figure 3).

 The moment is transmitted in a single stream. It differs from the previous transmission by the exception of the work of two pairs of gears: 8-4 and 5-9. On the intermediate shaft (Fig. 1), the moment is transmitted between the gear blocks by the clutch B.

 On the beam diagram, three rays: 3-7, 10-6, and vertical 13-17 reflect this transmission.

 Transmission 5. Switch clutch A to the right and clutch B to the left.

 The torque transmission corresponds to the second transmission stream 1.

 In the beam diagram, the rays of this transmission are shifted slightly to the left of the previous transmission: instead of beam 3-7, beam 5-9 is used.

 Transmission 6. Switch the clutch in the right position, all the clutch in the right position (figure 3).

 From the input shaft 2, the moment is transmitted by clutch A, a pair of gears 4-8, then, as in the previous gear.

 Compared to the previous two transmissions, the first beam 4-8 has shifted even more to the left from the rays 5-9 and 3-7 on the radiation diagram (figure 2).

 Transmission 7. We switch all couplings to the left position.

 The moment is transmitted in two ways, from gears 1 and 2 it differs in the direction of the second flow, clutch A is transmitted to a pair of gears 3-7, in block 7-8, a pair of gears 8-4, clutch B, gear 5, clutch C, and so on, as indicated gears (figure 1).

 In the beam diagram, rays 3-7, 8-4, 12-13-14, directed to point 7 on the axis of the gear ratio logarithm, indicate the second path of this transmission (Fig. 2).

 Transmission 8. Switch the clutch D to the right position.

 The moment is transmitted along the second stream of the previous transmission and is removed by the clutch D from the carrier 13.

 Three rays: 3-7, 8-4 and 13-17 indicate this transmission.

 Transmission 9. Switch clutch B to the right, and clutch D to the left position.

 The moment is transmitted in two streams, differs from transmission 7 by replacing a pair of gears 8-4 with a pair of gears 9-5.

 In the radiation diagram (figure 2) the second stream is represented by rays 3-7, 9-5 and 12-13-14, directed from point O to point 9 on the axis of the logarithm of the gear ratio.

 Transmission 10. Switch clutch D to the right position.

 The torque transmission corresponds to the second stream of the previous transmission, clutch D connects the carrier 13 of the planetary mechanism with the differential drive shaft 17.

 Three rays: 3-7, 9-5 and vertical beam 13-17 represent this transmission.

 Transmission 11 is direct. We switch clutch A to the right, and clutch B to the left position.

 The moment from the input shaft 2 by clutch A, gear 4, clutch B, gear 5, clutch C, shaft 12, carrier 13, clutch D is transmitted directly to the differential, including the direct transmission of torque to the shaft 22 of the drive axle of the rear bogie (Fig. .1).

 In the beam diagram, a vertical ray from point O to point 11 indicates this transmission (figure 2).

 Transmission 12. Switch clutch B to the right position.

 From the input shaft (Fig. 1), the moment of clutch A is transmitted to a pair of gears 4-8, then by clutch B to a pair of gears 9-5, clutch C to shaft 12 and further, as in the previous gear.

 Rays 4-8, 9-5 and vertical 13-17 represent this transmission (figure 2).

 Transmission 13. Switch the clutch D to the left position.

 The moment is transmitted in two ways: the first path coincides with gears 1, 2, 7 and 9, the second path corresponds to the second thread of the previous gear.

 In the radiation diagram (figure 2), rays 4-8, 9-5, 12-13-14, as well as beam 2-15-14 to point 13 represent this transmission.

 Reverse. With an increase in the difference in rotation speeds of the sun gear 15 and carrier 13, the deceleration of the rotation of the epicyclic wheel 16 increases (Fig. 2, points 9, 7, 2, and 1 below), with a further increase in this difference, the direction of rotation of the epicyclic wheel changes, we obtain the reverse gear.

 Transmission 1. Clutches A, B and D in the left position, and the clutch C in the right position (figure 3).

 The moment is transmitted in two streams. The first stream, like all summing gears: 1, 2, 7, 9, 13, The second thread corresponds to forward gear 3.

 In the beam diagram, this transmission is represented by beams 3-7, 8-4, 5-9, 10-6 and gentle 12-13-14 tense up to the right to point 1 on the axis of the logarithm of the gear ratio of the reverse gear, the second beam 2 approaches this point -15-14, reflecting the first stream of transmission of the moment (figure 2).

 Transmission 2. Switch the clutch in the right position (figure 3).

 The moment is also transmitted in two streams. The second stream corresponds to forward gear 4.

 Three beams: 3-7, 10-6 and 12-13-14 to point 2 on the axis of the logarithm of the reverse gear ratio represent the second stream of this transmission, beam 2-15-14 reflects the transmission of the moment by the first stream (figure 2).

 The nature of the gear distribution changes with other gear ratios of the gear pairs and the planetary gear.

 The economic effect is expressed in improving the operational characteristics of the vehicle due to the expansion of the kinematic capabilities of the Republic of Kazakhstan while reducing its metal consumption when using 8 gears and a planetary mechanism, instead of 16 gears, 13 forward gears in a wider range of gear ratios were received. Gear shifting is facilitated, since in the gearbox the intervals between gears are small, the range has been expanded due to the transforming capabilities of the planetary mechanism, transmission efficiency by reducing the pairs of gears transmitting the load, one of the most commonly used gears allows direct transmission of torque to the rear axle carriage.

Claims (1)

 DISTRIBUTION BOX containing a housing, shafts mounted on it with bearings, gears mounted on them, couplings, characterized in that three separate gears are freely mounted on the input shaft, and a planetary gear sun gear is fixed to the shaft output, a tubular drive shaft is located on the input shaft drove the planetary gear, the fourth gear is freely mounted on the tubular shaft, while all freely installed gears are engaged with gears combined in two blocks and freely mounted on p the intermediate shaft, between the gear blocks there is a coupling interconnected with a second, similar coupling located between the middle gears of the input shaft, two couplings are installed on the hubs located between the individual gears on the primary and tubular shafts, the differential drive shaft is located coaxially with the primary shaft, the outputs of the sun gear and the epicyclic wheel of the planetary gear are installed on it, and a hub with a clutch is fixed, one of the differential gears is fixed to the output shaft, the mouth aligned coaxially with the input shaft, the second differential gear is connected via a tubular shaft to the gear on which the differential lock clutch is mounted, wherein said gear is engaged with the gear fixed to the countershaft.

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