RU2385431C1 - Offset shaft- planetary gear box - Google Patents

Abstract

FIELD: machine building.

SUBSTANCE: eight step offset shaft- planetary gear box consists of 6 gears, of elementary three-link planetary mechanism, dual coupling and two clutches of gear shift. Input shaft (2) and primary shaft (3) are coaxially arranged in supports of case (1) of the gear box. Secondary shaft (4) is mounted parallel to coaxial shafts (2) and (3), while coaxially to shaft (4) there are located output shaft of carrier (5) and output shaft (6) of the assembly. Tubular shaft (7) with gear (8) engaging gear (9) is mounted of primary shaft (3). Block of gears (9) and (10) is freely assembled on secondary shaft (4) whereon there is also freely installed gear (11). Gear (10) of the block engages gear (12) secured on primary shaft (3). Gear (13) is also secured on primary shaft (3) and engages gear (11) of secondary shaft (4). Carrier (14) is fixed on output shaft (5), while sun gear (15) is fixed on secondary shaft (4). Epicyclical gear (16) with tubular shaft (17) is connected with tooth crown (18). Sun gear (15) engage satellites (19) arranged on axles of carrier (14); the satellites are engaged with epicyclical gear (16). Two-position tooth crown (20) of carrier (14) is secured on output shaft of carrier (5); while three-position tooth crown (21) is mounted on output shaft (6). Three-position clutch (22) is installed on tooth crown (21) and is movably connected with slider (23) with fork; double-sided tooth crowns (24) are assembled on the slider; with their external crown they engage tooth crown (25) of the assembly case (1). Three position clutch (26) is mounted on secondary shaft (4) between the second and the third row of gears. Driven disks (27) of left coupling are arranged on primary shaft (3), while driven disks (28) of the right coupling are arranged on tubular shaft (7).

EFFECT: expanded operational functionality of vehicle.

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Description

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

Known transmission units with a step change in gear ratios, containing gears, shafts, bearings, gear shifting devices used in domestic and foreign cars. (Automobiles: Construction, Design and Calculation. Transmission. / Ed. By A.I. Grishkevich. Mn .: Vysh. Shk., 1985. - 240 s).

These units are structurally complex, metal-intensive.

Closest to the proposed gearbox (KP) is KP according to patent RU 2295456 C1 (Bull. No. 8 of 03.20.2007).

The gearbox contains an aggregate housing in which a two-shaft non-axial gearbox with three pairs of external gears is located, all gears on the shafts are mounted freely, on each shaft two gears are combined into blocks, and one gear is installed separately, three-position gears are located between these gears and gear blocks switching clutch, the sun gear of a simple three-link planetary gear (PM) is fixed to the output of the secondary shaft of a two-shaft gearbox, the output shaft of the carrier and the output shaft of the unit aligned, the carrier and the epicyclic casing have adjacent gears, the tubular shaft of the epicyclic wheel housing, the carrier output shaft and the output shaft of the unit have adjacent gears, a three-position shift clutch is installed on the gear of the output shaft of the unit, the gear shaft of the output shaft of the carrier is on-off , the gear crown of the output shaft of the unit is three-position, the shift clutch on this crown has three internal gear rims, on the slide of the switch clutch about fixed gear ring with internal and external gearing, the external gearing of which is associated with a three-position gear ring of the unit body.

The described gearbox is simpler than the typical designs of transmission units listed in the book, provides a sufficient range of gear ratios (the ratio of gear ratios of the lowest gear to the highest), but has operational limitations on the passability of the vehicle and ease of control due to a break in the power flow when shifting gears.

The problem to which the invention is directed, is to expand the operational capabilities of the vehicle due to pairwise gear changes with virtually no disruption of the power flow.

The problem is solved by achieving a technical result, which consists in improving the process of gear shifting by installing dual clutch.

The problem to which the invention is directed, is to expand the operational capabilities of the vehicle due to pairwise gear changes with virtually no disruption of the power flow.

The specified technical result is achieved by the fact that the non-coaxial all-planetary gearbox contains an assembly body in which a two-shaft non-coaxial gearbox with three pairs of gears of external gearing are located, two gears on the secondary shaft are combined into a block, one gear is installed freely, there is a three-position gear between this gear and the gear block switching clutch, the sun gear of a simple three-link planetary mechanism is fixed at the output of the secondary shaft of a two-shaft gearbox, the output shaft is the sludge and the output shaft of the unit are coaxial, the carrier and the casing of the epicyclic wheel have adjacent gears, the tubular shaft of the body of the epicyclic wheel, the output shaft of the carrier and the output shaft of the machine have adjacent gears, a three-position switching clutch, gear is installed on the gear ring of the output shaft of the unit the drive shaft of the drive shaft is on-off, the gear ring of the output shaft of the unit is three-position, the shift clutch on this crown has three internal gear rings, on the floor gear shift ring with internal and external gearing, the external gearing of which is connected with a three-position gear ring of the unit body, rigidly fixed to the gearshift clutch, two gears are mounted on the input shaft and driven clutch discs are installed, between them on the input shaft there is a tubular shaft on which driven clutch discs are installed and the gear is fixed, the gears of the primary and tubular shafts are engaged with the gear block of the secondary shaft, the input shaft is located coaxially with the primary shaft replennym on the body it dual clutch with the drive plate.

The proposed technical solution allows you to change gears in pairs (8 and 7, 6 and 5, 4 and 3, 2 and 1) practically without interrupting the power flow, which facilitates the process of driving a vehicle and increases its throughput.

Figure 1 shows the kinematic diagram of an eight-stage non-coaxial all-planetary gearbox 8R4 2СЦ (8 forward gears and 4 reverse gears, dual clutch), containing 6 gears, a simple three-link planetary gear (PM), dual clutch and two gearshift clutches. The lower part shows the numbers of pairs of forward gears (1-3).

Figure 2 shows the radiation diagram of this gearbox with tables of clutch positions and shift clutches in various forward gears (8-1 at the top) and reverse gear (4R-1R at the bottom). In the upper part of the tables the pairs of gears (1-3) included in the work and the PM operation mode (I, II. III) are indicated. On horizontal scales, the gear ratios of gear pairs and gears are shown in a logarithmic form. The upper and lower horizontal correspond to gear ratios on the input, primary and output shafts, the middle horizontal - on the secondary shaft. The numbers of the pairs of gears are indicated on the beams. The greater the tilt of the beam to the right, the greater the gear ratio. The left tilt of the beam indicates the accelerating mode of the pair of gears. The tilt of the beam of each pair of gears is constant on any part of the radiation diagram.

The input shaft 2 and the input shaft 3 are coaxially located in the bearings of the gearbox housing 1. The secondary shaft 4 is installed parallel to the coaxial shafts 2 and 3, and the carrier shaft 5 and the output shaft 6 of the unit are located coaxially with it. On the primary shaft 3, a tubular shaft 7 is freely mounted on which the gear 8 is fixed, engaged with the gear 9. The gear unit 9 and 10 is freely mounted on the secondary shaft 4, on which the gear 11 is also freely mounted. The gear wheel 10 of the block is engaged with the gear 12 fixed on the input shaft 3. The gear 13 is also mounted on the input shaft 3 and engaged with the gear 11 of the secondary shaft 4. The carrier 14 is fixed on the output shaft 5, and the sun gear 15 is fixed on the secondary shaft 4. The epicyclic wheel 16 PM is connected by a tubular shaft 17 to the cog the crown 18. The sun gear 15 is engaged with the satellites 19 mounted on the axles of the carrier 14, which are also engaged with the epicyclic wheel 16. On the output shaft of the carrier 5, a two-position gear ring 20 of the carrier 14 is fixed, and a three-position gear ring is located on the output shaft 6 21. The three-position clutch 22 (B) is mounted on the ring gear 21 and is movably connected to the slide 23 with a fork, on which the double-sided ring gears 24 are located, the outer ring gearing with the ring gear 25 of the unit body 1. The three-position coupling and 26 (A) is mounted on the secondary shaft 4 between the second and third row of gears. Driven discs 27 of the left clutch (L) are mounted on the input shaft 3, and driven discs 28 of the right clutch (P) are mounted on the tubular shaft 7. On the input shaft 2 the dual clutch housing 29 is fixed, the drive clutch discs 30 are located on it. pressing leading 30 and driven 27 and 28 disks when engaging clutches, not shown.

The operation of the gearbox is carried out as follows: the dual clutch is triggered at each shift, which occurs almost without interrupting the power flow, clutch A changes its position after two shifts, and clutch B after four consecutive shifts. PM allows you to implement three modes of operation with the optimal gear shift mode: IU ^h _ab = -K; II-U ^b _ah = K + 1; III-U _(bh) = 1

First gear. Clutch A in the right position (P), clutch B in the second position (II) works the right clutch (P) (see figure 2, table. Right above t. 1). The epicyclic wheel 16 PM is stopped relative to the casing of the unit 1 with a double-sided gear ring 24, which is engaged with the outer ring with the gear ring 25 of the housing 1, and the inner ring with the ring gear of the body of the epicyclic wheel 16.

The torque from the drive shaft 2 (see Fig. 1) is transmitted through the right clutch (P) to the tubular shaft 7, then by a pair of gears 8-9, a gear block 9 and 10, through a pair of gears 10-12 to the input shaft 3, then a pair of gears 13-11 along clutch A to the secondary shaft 4, then to the sun gear 15, satellites 19, which, rolling around the locked epicyclic wheel 16, rotate the carrier 14 and the carrier shaft 5, then through gear ring 20 through coupling B to gear ring 21 and the output shaft of the unit 6 (see the lower position of the coupling In figure 1 on the right).

In the radiation diagram (see figure 2), this transmission is represented by rays: beam 1 leaves t.0 on the lower horizontal and is directed upward to the middle horizontal, then beam 2 is right downward to the lower horizontal, beam 3 is rightward upward to the middle horizontal and PM beam right up to t. 1.

Second gear. We switch the dual clutch, the left clutch (L) works.

The torque through the left clutch (L) is transmitted to the input shaft 3 and a pair of gears 13-11, then as in the previous gear.

On the beam diagram, this transmission is characterized by two beams: beam 3 from t.0 to the middle horizontal and the PM beam right up to t.2.

Third gear. We turn on the right clutch, switch clutch A to the left position.

The torque from the tubular shaft 7 is transmitted to a pair of gears 8-9, the gear unit 9 and 10, then through the clutch A to the secondary shaft 4, then as in previous gears.

On the beam diagram, this transmission belongs to two beams: beam 1 from t.0 to the middle horizontal and the PM beam right up to t.3.

Fourth gear. We switch the dual clutch, the left clutch works.

Torque through the left clutch is transmitted to the input shaft 3 and a pair of gears 12-10, further as in previous gears.

On the beam diagram, this transmission is characterized by two beams: beam 2 from t.0 to the middle horizontal and the PM beam right up to t.4.

Fifth gear. We engage the right clutch, clutch A in the right position, and clutch B in the third position (III). PM is blocked, as the coupling 22 (B) closed the ring gear 18 of the tubular shaft 17 of the epicyclic wheel 16 with the ring gear 20 of the output shaft 5 of the carrier 14.

The torque from the drive shaft 2 to the sun gear 15 is transmitted as in first gear, then through the sun gear 15, the satellites 19 and the locked epicyclic wheel 16 with the carrier 14 to the gear rings 18 and 20, then through the coupling B to the gear ring 21 and the output shaft 6.

In the ray diagram, this transmission is represented by rays: beam 1 leaves t.0 on the lower horizontal and is directed upward to the middle horizontal, then beam 2 is right down to the lower horizontal, beam 3 is right up to the middle horizontal and PM beam is vertically up to t. 5.

Sixth gear. We switch the dual clutch, the left clutch works.

The torque to the sun gear 15 is transmitted as in second gear, then as in the previous gear.

On the beam diagram, this transmission is characterized by two beams: beam 3 from t.0 to the middle horizontal and PM beam vertically up to t.6.

Seventh gear. We turn on the right clutch, switch clutch A to the left position.

The torque from the tubular shaft 7 is transmitted to a pair of gears 8-9, then through the clutch A to the secondary shaft 4, then in fifth gear.

On the beam diagram, this transmission belongs to two beams: beam 1 from t.0 to the middle horizontal and PM beam vertically up to t.7.

Eighth gear. We switch the dual clutch, the left clutch works.

Torque through the left clutch is transmitted to the input shaft 3 and a pair of gears 12-10, then as in the previous gear.

On the beam diagram, this transmission is characterized by two beams: beam 2 from t.0 to the middle horizontal and PM beam vertically up to t. 8.

To engage reverse gears, it is necessary to move the clutch B to the first position (I), thereby stop the carrier 14. The satellites 19, rotating on the axes of the stopped carrier 14, change the direction of rotation of the epicyclic wheel 16 relative to the sun gear 15.

First reverse 1R

Clutch A in the right position (P), clutch B in the first position (I), the right clutch (P) is working (see table below, Fig.2).

The torque to the sun gear 15 is transmitted in both first and fifth forward gears, from the epicyclic wheel 16 through the tubular shaft 17 to the ring gear 18, then through the ring gear 18 through the coupling B to the ring gear 21 and the output shaft 6 (see upper state clutch B in figure 1 on the right).

In the ray diagram, this transmission is represented by rays: beam 1 leaves t.0 on the lower horizontal and is directed upward to the middle horizontal, then beam 2 is right down to the lower horizontal, beam 3 is right upwards to the middle horizontal and PM beam is right down to t. 1R.

Second Reverse 2R

We switch the dual clutch, the left clutch works.

The torque to the sun gear 15 is transmitted in both second and sixth forward gears, further as in the previous gear.

On the beam diagram, this transmission is characterized by two beams: beam 3 from t.0 to the middle horizontal and the PM beam right up to t.2R.

Third Reverse 3R

We turn on the right clutch, switch clutch A to the left position.

The torque to the sun gear 15 is transmitted in both third and seventh forward gears, further as in previous reverse gears.

On the beam diagram, this transmission belongs to two beams: beam 1 from t.0 to the middle horizontal and the PM beam right up to t.3R.

Fourth Reverse 4R

We switch the dual clutch, the left clutch works.

The torque to the sun gear 15 is transmitted in both fourth and eighth forward gears, further as in previous gears.

On the beam diagram, this transmission is characterized by two beams: beam 2 from t.0 to the middle horizontal and PM beam right up to t.4R.

Claims (1)

An off-axis all-planetary gearbox containing an assembly body in which a two-shaft off-axis gearbox with three pairs of gears of external gearing are located, two gears on the secondary shaft are combined into a block, one gear is installed freely, a three-position switching clutch is located between this gear and the gear block, at the output of the secondary the shaft of a two-shaft gearbox secures the sun gear of a simple three-link planetary mechanism, the output shaft of the carrier and the output shaft of the unit are aligned, in the sludge and the epicyclic casing have adjacent gears, the tubular shaft of the epicyclic casing, the carrier output shaft and the output shaft have adjacent gears, a three-position switching clutch is installed on the gear shaft of the output shaft of the unit, the gear shaft of the output shaft has a two-position gear ring the output shaft of the unit is three-position, the shift clutch on this crown has three internal gear rims, on the slide of the switch clutch the gear is rigidly fixed crown with internal and external gearing, the external gearing of which is connected with a three-position gear ring of the unit body, characterized in that two gears are fixed on the input shaft and driven clutch discs are installed, between them a tubular shaft is freely located on the input shaft, on which driven clutch discs are mounted and the gear is fixed, the gears of the primary and tubular shafts are engaged with the gear block of the secondary shaft, the input shaft with the double housing fixed to it is located coaxially with the primary shaft clutch with drive discs.

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