RU2721229C2 - Planetary gearbox 10r4 with twin clutch - Google Patents

Abstract

FIELD: machine building.

SUBSTANCE: proposed gearbox comprises three-link planetary gear. Double-clutch housing is jointed to the casing, while shafts of input, primary and sun gears are coaxially mounted in bearings of housings and walls. In housing of clutch on input shaft there is crankcase with internal partition, clutch disks are movable in axial direction: driven on crankcase, driven discs of left clutch on primary shaft with three-gear rim and with clutch, driven discs of right clutch on drive tubular shaft, located on primary shaft, both shafts are engaged with the intermediate shaft, on the sun gears drive shaft with toothed rims at the ends the input and output tubular shafts of the carrier with toothed rims are freely installed, and on these shafts coaxial shafts of housing of epicyclic wheel also with toothed rims. On the walls of the planetary gear housing next to the gear rims of the input and output shafts there are fixed gear rims with the carrier stop clamps or the epicyclic wheel, near toothed rims of output shafts there is a driving tubular shaft with toothed rim and clutch at input of shaft and drive gear with toothed rim at output of this shaft near toothed rim of sun gears shaft, on which clutch is located, near to gear rim of rear wall of housing.

EFFECT: improved operational characteristics of gearbox.

1 cl, 2 dwg

Description

The invention relates to transport engineering, to the transmission of transport vehicles, to the STS (ground transportation systems), including TTM (transport and technological vehicles), cars, tractors, etc.

Transmission aggregates are known - gearboxes (gearboxes) with step change of gear ratios, containing gears, shafts, bearings, gear shifting devices used on domestic and foreign cars. (1. Osepchugov V.V., Frumkin A.K. Automobile: Structural analysis, calculation elements. - M.: Mashinostroenie, 1989. - 304 p. 2. Nekrasov V.I. Multistage transmission. Design, construction and calculation: Textbook.- Kurgan, Publishing House of the Kurgan State University, 2001. - 155 s)

These units are structurally complex and metal-intensive.

Modern NTS require the use of manual gearboxes (multi-stage gearboxes), which, due to the selection of the required gear ratio in the transmission, provide the possibility of the internal combustion engine (internal combustion engine) operating at optimum speed with minimal fuel consumption and the release of environmentally harmful substances.

MCPs, as a rule, are created on the basis of the basic 5-speed gearbox of the traditional layout, which are widely used both in the longitudinal (1. Fig. 37, p. 61; Fig. 35, p. 59) and transverse (1. Fig. 34, p. 58) the layout of the transmission. They can be three-shaft (1. Fig. 37, p. 61) or two-shaft (1. Fig. 35, p. 59; Fig. 34, p. 58).

To create a manual gearbox, two schemes are used: 1. installing the front divider in front of the base gearbox, doubling the number of gears (1. Fig. 41, p. 64); 2. Installing the rear gearbox-demultiplicator behind the base gearbox, the gearbox can consist of two rows of cylindrical gears (2. Fig. 28, c, p. 45; Fig. 29, p. 47) or from a simple PM (planetary gear - 2. Fig. 27, p. 44; Fig. 28, d). Sometimes both schemes are simultaneously used (2. Fig. 31, p. 48). In the traditional layout, the clutch is installed between the internal combustion engine and gearbox, in this case, with the transverse layout of the internal combustion engine and the transmission of the engine, the main gear is shifted from the center of the NTS, the drive shafts of the drive wheels (axles) will have different lengths; replacement of the clutch discs is difficult, since in this case it is necessary to remove the transmission unit (MCP and GM).

Closest to the proposed device is a nine-speed KP NM3-201 with PM at the output (2. Fig. 27, p. 44; Fig. 28, d).

KP YaM3-201 is composed of a pine 5-step three-way base KP and planetary demultiplier. The basic gearbox consists of a housing in which the primary, secondary and output shafts are coaxially located, and an intermediate shaft is installed parallel to them. On the shafts of the base gearbox there are five rows of forward gears and a row of reverse gears, between the gear rows there are three shift clutches, two of them with synchronizers.

The drawback of the KP of the traditional layout is that for each forward gear they require their own pair of gears, and for reverse gear three or four gears. Rows of gears increase the longitudinal dimension and the metal consumption of the gearbox. Spur gears have limited load capacity due to single-pair (single-threaded) gearing, while increasing the transmitted torque it is necessary to increase the center-to-center (center-to-center) distance, which increases the transverse dimensions of the gearbox.

The requirement of reducing the metal consumption of machines from all types of mechanical gears is most fully satisfied by planetary gears, which are characterized by small dimensions and weight. This is due to the multithreading effect and the use of internal gearing.

A simple PM (planetary mechanism) consists of three links: the sun gear (a), the epicyclic wheel (b) and the carrier (h) with satellites.

PM is characterized by an internal parameter K = Z _b / Z _a = 1.5-5, which is equal to the ratio of the number of teeth of the epicyclic wheel Z _b to the number of teeth of the sun gear Z _a . A smaller value of K is limited by the minimum dimensions of the satellites, a larger value is limited to the sun gear.

Simple PM, in addition to the differential, is mainly used as a single-stage wheel gearbox of a double spaced main gearbox (main gear) of the vehicle’s drive axle (1. Fig. ON, p. 138) or a two-stage gearbox - a demultiplier at the MCP output (2. Fig. 27, p. 44; Fig. 28, d).

The disadvantage of such a PM is that it implements only two gears: a direct one when the PM is blocked due to the connection of a clutch between two links: the epicyclic wheel (b) and the carrier (h) and slow in the mode U _ah ^b = K + 1. Where U is the gear ratio, the index at the top is the stopped link, the indices at the bottom are the input and output links of the torque. The epicyclic wheel (b) is stopped, the torque is applied to the sun gear (a) and removed from the carrier (h).

The problem to which the invention is directed, is to reduce the size and metal consumption of the NTS transmission unit while improving the layout and operational characteristics.

The problem is solved by making better use of the kinematic capabilities of a simple three-link PM, installing a dual clutch and a front splitter at the PM input.

The essence of the proposed device lies in the fact that the gearbox contains a housing with shafts installed in it, rows of external gears and a gear shift clutch, a simple three-link planetary mechanism consisting of a carrier with satellites engaged with a sun gear and an epicyclic wheel, a carrier and an epicyclic casing the wheels have shafts with gear rims and a clutch for stopping the epicyclic wheel, while the dual clutch case is attached to the gearbox housing with internal walls, shafts are installed coaxially in the supports of these cases and walls: input, primary and sun gear drives; in the dual clutch housing, a crankcase with an internal baffle is installed on the input shaft, the clutch discs are axially movable: leading relative to the crankcase, left clutch discs on the input shaft with a three-position gear ring and with a clutch, right clutch discs on the drive tubular shaft located on the input shaft, on these shafts gears are fixed, engaged with gears fixed on the intermediate shaft, on the drive shaft of the sun gear with gear rims, the input and output tubular shafts of the carrier with gear rims are freely mounted on the ends, and on these shafts are the coaxial shafts of the epicyclic wheel housing also with serrated gears; on the walls of the planetary gear housing, next to the gear rims of the input and output shafts, gear rims with a stop carrier or an epicyclic wheel are fixed; next to the gear rims of the output shafts, a drive tubular shaft with a gear rim and a shift clutch at the input shaft and a drive gear with a gear rim on the output of this shaft next to the gear rim of the sun gear shaft, on which the switching clutch is located, next to the gear rim of the rear wall of the housing.

The proposed technical solution provides ten forward gears and four reverse gears with a sufficient range (D = U ₁ / U ₁₀ = 3.35 / 0.38 = 8.8) equal to the ratio of gear ratios of lower and higher gears; an interval of 1.27; convenient for gear shifting, and dual clutch, allowing to change gears in pairs practically without breaking the power flow, while reducing dimensions and metal consumption in comparison with standard designs.

In FIG. 1 shows a diagram of a gearbox (gearbox) with dual clutch, with a front splitter and a simple three-link PM (planetary gear), which has five switching clutches, input, output and stop shafts of three PM links with gear rims. In the upper part of the clutch, they are shown in the state of the 1st forward gear U _ah ^b , in the lower part - the 4th reverse gear 4R U _ba ^h .

In FIG. 2 shows the radiation diagram of the KP for K = 1.62. A change in the value of the internal parameter K leads to a change in the kinematic characteristics of the KP. When K = 1.62, we obtain equal segments between the transmissions on the horizontal scale in a logarithmic scale lq 1.62 = 0.21, where the values of the gear ratios of the PM are postponed. The front divider equally divides the segments between gears. A vertical beam indicates a direct transmission of torque from the engine to the drive gear of the GP drive (final drive). The beam to the right upwards characterizes the decelerating mode of operation of the PM, the more positive the beam, the higher the gear ratio. A beam up to the left characterizes the accelerating mode of operation of the PM, the more positive the beam, the lower the gear ratio. Beam diagrams are convenient for understanding the operation of the CP, since the magnitude of each ray is constant in all parts of the diagram. Above the beam diagram is a table of the positions of the shift clutches in various gears. The upper part of the table shows the state of the PM on each gear and the PD (front divider). Below the position of the clutch: A - E.

A dual clutch housing 6 is attached to the gearbox housing (gearbox) 1 with internal walls 2 to 5. An input shaft 7, a primary shaft 8, a sun gear drive shaft 9 are installed in the bearings of the housings and walls 1 to 6, and an intermediate shaft 10 is located parallel to them on which gears 11 and 12 are fixed. On the input shaft 8, a tubular drive shaft 13 is freely mounted, on which the drive gear is fixed 14. On the input shaft 8, the gear 15 and the three-position gear ring 16 are fixed, and the drive disks 17 of the left are mounted movably in the axial direction clutch. On the tubular drive shaft 13 is also movable in the axial direction mounted driven discs 18 of the right clutch. A dual clutch housing 19 is fixed to the input shaft 7 with an internal baffle 20 and axially movable drive disks 21. At the ends of the shaft 9, the input gear 22 and the output 23 gear rims of the middle part of the shaft 9 are fixed, the sun gear 24 (a) is fixed, which is engaged by the satellites 25 drove 26 (h) with an epicyclic wheel 27 (c). Tubular shafts of carrier 26 (h) are installed on shaft 9: input shaft 28 with gear ring 29 and output shaft 30 with ring gear 31. At the input of the housing 32 of the epicyclic wheel 27 (b), the input coaxial shaft 33 with ring gear 34 is fixed, and the output is the output coaxial shaft 35 with the ring gear 36. Above the input coaxial shaft 33 on the front inner wall 3, next to the ring gear 34, there is a three-position ring gear 37, on the rear inner wall 4 next to the ring gear 36 there is a three-position ring gear 38. On the shaft 9, a leading tubular shaft 39 with a three-position gear ring 40 at the input of this shaft and with a pinion gear 41 of the main gear (main gear) with a ring gear 42 at the output of the driving shaft 39 is installed in the support of the inner wall 5 near the gear ring 31. The GP can be cylindrical as in FIG. 1, conical, hypoid. Opposite the ring gear 42, next to the ring gear 23 of the shaft 9, the ring gear 43 is located on the rear wall of the gearbox housing 1. The three-position shift clutch 44 (A) is mounted on the three-position ring gear 16 at the output of the input shaft 8 for selectively connecting to the ring gear 22 of the sun gear drive 24 (a), with a gear ring 29 drive drove 26 (h), with a gear ring 34 drive epicyclic wheels 27 (b). The shift clutch 45 (B) is located on the ring gear 37 of the front inner wall 3 for stopping the carrier 26 (h) with the ring gear 29 or the epicyclic wheel 27 (b) with the ring gear 34, a neutral (H) - off state is ensured by installing the coupling between the ring gears 29 and 34 or by moving it to the wall 3. The clutch 46 (C) is located on the ring gear 38 of the rear inner wall 4 to stop the carrier 26 (h) ring gear 31 or the epicyclic wheel 27 (b) ring gear 36, neutral (H) - the off state is ensured by the installation of the coupling between the gear rims 36 and 31 or its movement to the wall 4. The couplings 45 (B) and 46 (C) partially overlap one another. The shift clutch 47 (D) is mounted on the gear ring 40 of the input of the driving tubular shaft 39 for selectively connecting with the gear ring 36 of the output coaxial shaft 35 of the epicyclic wheel 27 (b) or with the gear ring 31 of the output tubular shaft 30 of carrier 26 (h), neutral ( H) the condition is ensured by the installation of the coupling between the crowns 36 and 31 or its movement to the extreme right position (Fig. 1, below). The clutch 48 (E) is located on the ring gear 23 at the output of the shaft 9 of the sun gear 24 for driving the pinion gear 41 when connected to the ring gear 42 or to stop the sun gear 24 when connecting to the ring gear 43 of the rear wall of the gearbox housing 1.

At the output of the shaft 9 it is possible to install a PTO (power take-off shaft), for example, to drive a winch, etc. The clutch shift mechanism can be either hydraulic or mechanical.

The gearbox works as follows: dual clutch is triggered at each shift, which occurs almost without interruption in the power flow. If, for example, a working fluid is supplied between the inner partition 20 and the drive disk 21 left of it, then the left (L) clutch is actuated, in which the drive wheels 21 press the drive wheels 17, which includes the input shaft 8 and the gear clutch 16. If , for example, to supply the working fluid between the inner partition 20 and the drive disk 21, which is right from it, then the right (P) clutch is activated, which with the driven disks 18 includes the PD (front splitter): the first pair of gears (14-11), countershaft 10 and the 2nd pair of gears (15-12).

A simple three-link PM (planetary gear) can provide five gears without changing the direction of rotation, two reverse gears and three gears in integral (summing) modes, when the torque is applied to two PM links with different rotational speeds, and is removed from the third link. In the considered KP, we do not use integral (summing) modes. When K = 1.62 we get:

1st gear PM: U _ah ^b = K + 1 = 2.62; lq 2.62 = 0.42;

2nd gear PM: U _bh ^a = (K + 1) / K = 2.62 / 1.62 = 1.62; lq 1.62 = 0.21.

3rd gear PM: Direct U = 1,0; lq 1.0 = 0.0.

4th gear PM: U _hb ^a = K / (K + 1) = 1.62 / 2.62 = 0.62; lq 0.62 = -0.21.

5th gear PM: U _ha ^b = 1 / (K + 1) = 1 / 2.62 = 0.38; lq 0.38 = -0.42.

1st reverse gear PM: U _ab ^h = -K = 1.62; lq 1.62 = 0.21;

2nd reverse gear PM: U _ba ^h = - (1 / K) = 1 / 1.62 = 0.62; lq 0.62 = -0.21.

A minus sign indicates a change in the direction of rotation at the output compared to the input.

The front divider halves the 1.62 interval:

U _pd = (1.62) ^0.5 = 1.273; lq 1.273 = 0.105.

The device operates as follows.

First gear

In the beam diagram (Fig. 2), this mode is indicated by three beams: a steep beam from t. 0 to the right down, then a steep beam to the right up, then a gentle beam to the right up to t. 1.

Above this point, the states of the switching clutches are shown (see Fig. 1, the upper position of the couplings): A and C - left (L), B and D - right (P), E - neutral (H). The upper part of the table shows U _ah ^b = K + 1 state of the PM. Front splitter in downshift, right (P) clutch engaged.

The epicyclic wheel 27 (b) is stopped by a coupling 45 (B), which closes the gears 37 of the front inner wall 3 and 34 of the tubular shaft 33 of the housing 32 of the epicyclic wheel 27. Torque (Fig. 1) from the drive shaft 7, the drive discs 21 and the driven the right clutch disks 18 are transmitted to the drive tubular shaft 13, a pair of gears 14-11, an intermediate shaft 10, a pair of gears 12-15, a primary shaft 8 and a gear ring 16, then a clutch 44 (A) to a ring gear 22, a shaft 9 to the sun gear 24 (a). The sun gear 24 (a) rotates the satellites 25, which, rolling around the epicyclic wheel 27 (b), rotate the carrier 26 (h) with a reduced frequency, but with increased torque. Tubular shaft 30, ring gear 31, clutch 47 (D) torque is supplied to ring gear 40, to the leading tubular shaft 39 and the driving gear GP 41.

When K = 1.62 gear ratio 1st gear

Second gear

In the beam diagram (Fig. 2), this mode is indicated by a gentle beam from t. 0 to the right up to t. 2.

We switch the clutch from the right position to the left (L) - the front divider goes into the direct transmission position. The state of the PM did not change U _ah ^b = K + 1.

The torque (Fig. 1) from the clutch drive disks 21 by the driven disks 17 is transmitted to the input shaft 8 and the ring gear 16, by the coupling 44 (A) to the ring gear 22, then in the 1st gear.

When K = 1.62 gear ratio 2nd gear

Third gear

In the beam diagram (Fig. 2), this mode is indicated by three beams: a steep beam from t. 0 to the right down, then a steep beam to the right up, then a steep beam to the right up to t. 3.

We return the clutch in the 1st gear position (P), clutch A from the left position to the right (P), clutch B from the right position to neutral (H) - off - to the body wall 3, clutch C from the left position to neutral (H ), clutch E from neutral to right (P). The upper part of the table shows the U _bh ^a state of the PM. In comparison with the 1st gear, the links were replaced: the sun gear 24 (a) was stopped, the torque is supplied to the epicyclic wheel 27 (b).

The sun gear 24 (a) is stopped by the clutch 48 (E), which closed the gear rims 43 of the rear wall of the gearbox housing 1 and 23 of the shaft 9. The torque from the right clutch to the gear rim 16 is transmitted as in 1st gear. Then the clutch 44 (A) is transmitted to the ring gear 34 and the coaxial shaft 33 through the housing 32 to the epicyclic wheel 27 (b) which rotates the satellites 25, they, rolling around the sun gear 24 (a), rotate the carrier 26 (h), hereinafter referred to as in 1st gear.

When K = 1.62 gear ratio 3rd gear

Fourth gear

In the beam diagram, this mode is indicated by a steep ray from t. 0 to the right up to t. 4.

We switch the clutch from the right position to the left (L) - the front divider goes into the direct transmission position. The state of the PM has not changed U _bh ^a .

Torque (Fig. 1) from the drive clutch discs 21 by driven discs 17 is transmitted to the shaft 8, to the ring gear 16, then as in 3rd gear.

When K = 1.62 gear ratio 4th gear

Fifth gear

In the beam diagram (Fig. 2), this mode is indicated by three beams: a steep beam from t. 0 to the right down, then a steep beam to the right up, then a vertical beam to t. 5.

Return the clutch in the 1st and 3rd gear position (P), clutch A from the right to middle position (C), and clutch E from the right to neutral (H) position. At the top of the table shows the state of the PM - direct transmission.

Torque from the clutch to the ring gear 16 is transmitted in both 1st and 3rd gear. Then the clutch 44 (A) is transmitted to the ring gear 29 and the tubular shaft 28 to the carrier 26 (h), then as in the 1st and 3rd gear.

When K = 1.62, the gear ratio of the 5th gear

Sixth gear - direct

On the beam diagram, this transmission is represented by a vertical beam from t. 0 to t. 6.

The clutch is returned to the left (L) position.

The torque (Fig. 1) from the clutch drive disks 21 by the driven disks 17 is transmitted to the shaft 18, to the ring gear 16, then as in the 5th gear.

When K = 1.62, the gear ratio of the 6th gear is U _6n = 1.0

Seventh gear

In the beam diagram (Fig. 2), this mode is indicated by three beams: a steep beam from t. 0 to the right down, then a steep beam to the right up, then a steep beam to the left up to t. 7.

We return the clutch in the 1st, 3rd and 5th gear position (P), clutch D from the right to the left (L), and the clutch E from the neutral position to the right (P), while compared with the 3- The first transmission replaced the input and output torque links. The upper part of the table shows the U _hb ^a state of the PM.

Torque from the clutch to the ring gear 16 is transmitted as in 1st, 3rd and 5th gear. Then, the clutch 44 (A) is transferred to the ring gear 29 and the tubular shaft 28 to the carrier 26 (h), which rotates the satellites 25, they, rolling around the stopped sun gear 24 (a), rotate the epicyclic wheel 27 (b), along the body 32 on the coaxial shaft 35, the ring gear 36, the coupling 47 (D), the torque is supplied to the ring gear 40, the leading tubular shaft 39 and the driving gear GP 41.

When K = 1.62, the gear ratio of the 7th gear

lq 0.785 = -0.105

Eighth gear

In the beam diagram, this mode is indicated by a steep ray from t. 0 to the top left to t. 8.

Switch the clutch from the right to the left (L) position.

The torque (Fig. 1) from the clutch drive disks 21 by the driven disks 17 is transmitted to the shaft 8, to the ring gear 16, then in the 7th gear.

When K = 1.62, the gear ratio of the 8th gear

Ninth gear

In the beam diagram (Fig. 2), this mode is indicated by three beams: a steep beam from t. 0 to the right down, then a steep beam to the right up, then a gentle beam to the left up to t. 9.

Return the clutch in the 1st, 3rd, 5th and 7th gear positions (P), clutch B, switch from neutral to right (P), clutch C from neutral to left (L), clutch D from the left to the neutral (H) position, and the clutch E from the right to the left (L) position, while in comparison with the 1st gear, the input and output torque links were replaced. The upper part of the table shows the U _ha ^b state of the PM.

The epicyclic wheel 27 (b) is stopped by a coupling 45 (B), which closes the gears 37 of the front inner wall 3 and 34 of the coaxial shaft 35 of the housing 32 of the epicyclic wheel 27. The torque (Fig. 1) is transmitted to carrier 26 (h) as in 8 -th gear, which rotates the satellites 25, they, rolling around the stopped epicyclic wheel 27 (b), rotate the sun gear 24 (a), then along the shaft 9 to the ring gear 23, the coupling 48 (E) to the ring gear 42 and the drive wheel GP 41, but with an increased rotational speed and reduced torque.

When K = 1.62, the gear ratio of the 9th gear

Tenth gear

In the beam diagram, this mode is indicated by a gentle beam from T.O., from left to top, to T. 10.

Switch the clutch from the right to the left (L) position.

The torque (Fig. 1) from the clutch drive disks 21 by the driven disks 17 is transmitted to the shaft 8, to the ring gear 16, then in the 9th gear.

When K = 1.62, the gear ratio of the 10th gear

First reverse gear 1R On the radiation diagram (Fig. 2), this mode is indicated by three beams: a steep beam from t. 0 to the right down, then a steep beam to the right up, then a steep beam to the right down to t. 1R.

The states of clutch and shift clutches are shown in the rightmost column of the table below under 1R: clutch - right (P), A, B and D - left (L), C and E - neutral (H). The bottom part of the table shows the U _ab ^h = -K state of the PM. A minus sign indicates a change in the direction of rotation of the drive gear 41 compared to the input shaft 7. Compared to the 1st forward gear, the states of the output and stopped PM links have changed.

The carrier 26 (h) was stopped by the coupling 45 (B), which closed the gears 37 of the front inner wall 3 and 29 of the tubular input shaft 28. The torque (Fig. 1) is transmitted to the sun gear 24 (a) as in the 1st gear of the front move. The sun gear 24 (a) rotates the satellites 25, which, rotating on the axes of the carrier 26 (h), rotate the epicyclic wheel 27 (b) in the opposite direction with a lower speed, but with increased torque. Further, as in the 7th forward gear, coaxial shaft 35, ring gear 36, clutch 47 (D), torque is supplied to ring gear 40, to the leading tubular shaft 39 and the driving gear GP 41.

When K = 1.62, the gear ratio of the first reverse gear 1R

Second gear reverse 2R

In the beam diagram (Fig. 2), this mode is indicated by a steep beam from t. 0 to the right down to t. 2R.

We switch the clutch to the left (L) position, turned off the gears of the front divider.

The torque (Fig. 1) from the clutch drive disks 21 by the driven disks 17 is transmitted to the shaft 8, to the ring gear 16, then as in the 1st reverse gear.

When K = 1.62, the gear ratio of the second reverse gear 2R

Third gear reverse 3R

In the beam diagram (Fig. 2), this mode is indicated by three beams: a steep beam from t. 0 to the right down, then a steep beam to the right up, then a steep beam to the left down to t. 3R.

Return the clutch to the right (P) position, switch clutch A from left to right (P), couplings B and D to neutral (H), clutch C from neutral to right (P), and clutch E to left (L) . At the bottom of the table is shown the U _ba ^h state of the PM.

The carrier 26 (h) is stopped by the coupling 46 (C), which closed the gears 38 of the rear inner wall 4 and 31 of the tubular output shaft 30. The torque (Fig. 1) is transmitted to the epicyclic wheel 27 (b), as in 3rd gear forward course. The epicyclic wheel 27 (b) rotates the satellites 25, which, rotating on the axes of the carrier 26 (h), rotate the sun gear 24 (a) in the opposite direction with an increased speed, but with a reduced torque. Further, as in the 9th forward gear along the shaft 9 to the ring gear 23, the clutch 48 (E) to the ring gear 42 and the drive wheel GP 41, but with an increased speed and a reduced torque.

When K = 1.62, the gear ratio of the third reverse gear 3R

Fourth Reverse 4R

In the beam diagram (Fig. 2), this mode is indicated by a steep beam from t. 0 to the left down to t. 4R.

We switch the clutch to the left (L) position, the gears of the front divider are turned off from the work.

The torque (Fig. 1) from the clutch drive disks 21 by the driven disks 17 is transmitted to the shaft 8, to the ring gear 16, then as to the 3rd reverse gear.

When K = 1.62, the gear ratio of the fourth reverse gear 4R

The KP range is D = U ₁ / U ₁₀ = 3.35 / 0.38 = 8.8.

A change in K will change the kinematic characteristics of the KP.

Got a compact transmission unit of low metal consumption due to a significant reduction in the longitudinal dimension, which creates better conditions for the transverse layout of the engine and transmission. They ensured the expansion of the vehicle’s performance by increasing its cross-country ability and facilitating control due to the pairwise shifting of 10 forward gears and 4 dual-clutch reverse gears (1–2; 3–4, etc., up to 9–10) practically without breaking the power flow. Longitudinal arrangement is allowed in RTO mode (multi-stage transfer case). The center differential can be either symmetric (Fig. 1, bottom right) or asymmetric.

Designations:

1 - gearbox housing (gearbox);

2 - the inner wall of the gearbox for the front divider;

3 - the inner front wall of the PM (planetary gear);

4 - the inner back wall of the PM;

5 - the inner wall of the gearbox for the GP (main gear);

6 - dual clutch housing;

7 - input shaft; 8 - a primary shaft;

9 - a shaft of a drive of a sun gear;

10 - an intermediate shaft;

11, 12 - gears mounted on the intermediate shaft 10;

13 - leading tubular shaft freely mounted on the input shaft 8;

14 - the drive gear mounted on the drive tubular shaft 13;

15 - gear mounted on the input shaft 8;

16 - three-position gear ring on the output of the shaft 8;

17 - driven discs of the left clutch on the input shaft 8;

18 - driven discs of the right clutch on the drive tubular shaft 13;

19 - dual clutch housing mounted on the input shaft 7;

20 - the internal partition of the dual clutch housing 19;

21 - leading dual clutch discs 19;

22 - gear ring at the input of the shaft 9;

23 - ring gear at the output of the shaft 9;

24 (a) - sun gear PM (planetary gear);

25 - satellites on the axles drove 26;

26 (h) - carrier PM;

27 (b) - epicyclic wheel PM;

28 - tubular input shaft of carrier 26 (h);

29 - the gear ring of the shaft 28 at the entrance of the carrier 26 (h);

30 - tubular output shaft of carrier 26 (h);

31 - the ring gear of the shaft 30 at the exit of the carrier 26 (h);

32 - the body of the epicyclic wheel 27;

33 - input coaxial shaft of the housing 32 of the epicyclic wheel 27;

34 - the gear rim of the input coaxial shaft 33;

35 - output coaxial shaft of the housing 32 of the epicyclic wheel 27;

36 - the gear rim of the output coaxial shaft 35;

37 - three-position gear ring of the front inner wall 3;

38 - three-position gear ring of the rear inner wall 4;

39 - the leading tubular shaft of the drive pinion drive 41;

40 - three-position gear ring of the leading tubular shaft 39;

41 - driving gear GP (main transmission);

42 - ring gear at the output of the driving tubular shaft 39;

43 - the gear ring of the rear wall of the housing KP 1 next to the ring gear 23;

44 (A) - three-position switching clutch on the ring gear 16 at the output of the input shaft 8 of the front divider;

45 (B) - coupling stop links PM on the gear ring 37 of the front inner wall 3;

46 (C) - coupling stop links PM on the ring gear 38 of the rear inner wall 4;

47 (D) - switching clutch at the input of the driving tubular shaft 39;

47 (E) - switching clutch on the ring gear 23 at the output of the shaft 9 of the drive of the sun gear 24 (a).

Claims (1)

A gearbox comprising a housing with shafts installed in it, rows of external gears and a gearshift clutch, a simple three-link planetary mechanism consisting of a carrier with satellites engaged with a sun gear and an epicyclic wheel, a carrier and an epicyclic wheel body have shafts with gear rings and a clutch for stopping an epicyclic wheel, characterized in that a dual clutch housing is connected to the gearbox housing with inner walls, coaxially mounted in the supports of these housings and walls reinforced shafts: input, primary and solar gear drive; in the dual clutch housing on the input shaft there is a crankcase with an internal baffle plate, the clutch discs are axially movable: leading relative to the crankcase, left clutch discs on the input shaft with a three-position gear ring and with a clutch, right clutch discs on the drive tubular shaft located on the input shaft, on these shafts there are fixed gears engaged with gears fixed on the intermediate shaft, on the drive shaft of the sun gear with gear rims at the ends of the free set the input and output shafts tubular carrier with toothing, and on these shafts coaxial shafts and the housing epicyclic wheel with toothed rims; on the walls of the planetary gear housing, next to the gear rims of the input and output shafts, gear rims with a stop carrier or an epicyclic wheel are fixed; next to the gear rims of the output shafts, a drive tubular shaft with a gear rim and a shift clutch at the input shaft and a drive gear with a gear rim on the output of this shaft next to the gear rim of the sun gear shaft, on which the switching clutch is located, next to the gear rim of the rear wall of the housing.

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