RU2717289C2 - Planetary gearbox 13r12 - Google Patents

Abstract

FIELD: machine building.

SUBSTANCE: invention relates to transmissions of type 13R12. Three links of simple three-link planetary mechanisms (PM) - sun gear, epicyclic wheel and carrier with satellites - have shafts with toothed rims and eight clutches at input and output of two PM.

EFFECT: compactness of planetary gearbox 13R12 type (thirteen forward gears and twelve reverse gears) at reduction of overall dimensions and metal consumption.

1 cl, 2 dwg

Description

The invention relates to transport engineering, to the transmission of transport vehicles, to the NTS (ground transportation systems), including SDM (construction and road vehicles), tractors, cars, 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.: Mechanical Engineering, 1989. - 304 p. 2. Nekrasov V.I. Multistage transmission. Design, construction and calculation: Textbook.- Kurgan, Publishing House of the Kurgan State University, 2001. - 155 p.)

These units are structurally complex and metal-intensive.

Modern NTS require the use of gearboxes (gearboxes) with a wide range equal to the ratio of gear ratios of lower and higher gears, which, due to the choice of the required gear ratio in the transmission, provide the possibility of the internal combustion engine (internal combustion engine) operating at optimal mode with minimal fuel consumption and environmental emission harmful substances.

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 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 to reduce 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 effect of multithreading and the use of internal gearing.

Closest to the proposed device is the PCP (planetary gearbox) with two PM from hydromechanical transmission (1. Fig. 67, p. 92, 93).

The control panel is formed by two elementary planetary gears of the same parameters. The control panel consists of a housing in which the primary and secondary shafts are coaxially mounted. On the shafts of the control panel there are two rows of gears of simple three-link PM, as well as three friction clutches and two tape brake mechanisms.

The disadvantage of the design considered is that it provides only three forward gears and one reverse gear (1. p. 94).

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. 110, p. 138) or a two-stage gearbox - a demultiplier at the MCP output (2. Fig. 27, p. 44; Fig. 28, d).

The disadvantage of this PM is that it implements only two gears: direct when the PM is blocked due to the coupling between the gearshift of two links: the epicyclic wheel (b) and the carrier (h) and the slow 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 improve the operational characteristics of the NTS while reducing the size and metal consumption of the transmission unit.

The problem is solved by making better use of the kinematic capabilities of a simple three-link PM.

The essence of the proposed device lies in the fact that the planetary gearbox contains a housing with primary and secondary shafts installed in it, two simple three-link planetary mechanisms, each consisting of a carrier with satellites engaged with a sun gear and an epicyclic wheel, while in the bearings of the gearbox housing with inner walls between the primary and secondary shafts equipped with gear rims with switching clutches, shafts are mounted coaxially: drives of solar gears of planetary gears with an intermediate link between them with gear rims and two switching clutches; the input and output tubular shafts of the carrier with the gear rims are freely mounted on the shafts of the drive gear of the sun gear with gear rims on the ends; the coaxial shafts of the epicyclic wheel body with gear rims are located on the tubular shafts; on the walls of the housings of planetary gears next to the gear rims of the input and output shafts, gear rims with stop couplings of the carrier or epicyclic wheel are fixed.

The proposed technical solution, in comparison with standard designs, provides thirteen forward gears and twelve reverse gears with a high range of D = U ₁ / U ₁₃ = 10.0 / 0.1 = 100 with a decrease in dimensions and metal consumption, which ensures the expansion of operational and layout characteristics of the NTS.

In FIG. 1 shows a diagram of a control panel (planetary gearbox) with two simple three-link PM (planetary gears), input, output, and stop shafts of two PM links with gear rims and eight shift clutches. In the upper part of the shift clutch, the 1st forward gear is shown: both PM U _ah ^b , in the lower part is the 12th reverse gear: 1st PM U _ba ^h , 2nd PM U _ha ^b . Under the ring gears, their positions are shown in small print: L - left, C - middle, P - right. For example, the position of L is occupied by gear rims: 9, 29, 12 and 44; position C: 22, 24, 37 and 39; position P: 27, 10, 42 and 13.

In FIG. 2 shows a radiation diagram of the operation of the control panel for K ₁ = 3.0 and K ₂ = 1.5. On a horizontal scale on a logarithmic scale, the gear ratios of the gearbox are plotted. A vertical beam indicates direct transmission of torque. The beam to the right characterizes the decelerating mode of operation of the PM, the more positive the beam, the higher the gear ratio. The beam 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. The rays in FIG. 2 are located symmetrically relative to the vertical axis at the level of U = 1.0; lq 1.0 = 0.0. Above and below the beam diagram, tables of shift clutch positions for various gears are shown. The upper part of the table shows the states of two PM. Below are the positions of the eight shift clutches: A-H.

In the supports of the control panel housing (planetary gearbox) 1 with internal walls 2-5, shafts with gear crowns fixed to them are coaxially mounted. A crown 7 is fixed on the primary shaft 6, at the ends of the shaft 8 of the drive of the sun gear of the first PM, the input crown 9 and the output crown 10; at the ends of the shaft 11 of the drive of the sun gear of the second PM, the input crown 12 and the output crown 13, between them there is an intermediate link 14, equipped with gear crowns; a three-position crown 16 is fixed on the secondary shaft 15. In the middle part of the shaft 8, the sun gear 17 (a) of the first PM is fixed, which is engaged by the satellites 18 of carrier 19 (h) with an epicyclic wheel 20 (c). Tubular shafts of the carrier 19 (h) are freely mounted on the shaft 8: in the support of the inner wall 2, the input shaft 21 with the ring gear 22 and the output shaft 23 with the ring gear 24. At the input of the housing 25 of the epicyclic wheel 20 (b), the input coaxial shaft 26 is secured a ring gear 27, and at the output, an output coaxial shaft 28 with a ring gear 29. A ring gear 30 is located on the front inner wall 2 next to the ring gear 27, and a ring gear 31 is located on the rear inner wall 3 next to the ring gear 29. In the middle part shaft 11 fixed sun gear 32 (a) the second PM, which is engaged by satellites 33, drove 34 (h) with an epicyclic wheel 35 (c). Tubular shafts of carrier 34 (h) are freely mounted on the shaft 11: in the support of the inner wall 4, the input shaft 36 with the ring gear 37 and the output shaft 38 with the ring gear 39. The input coaxial shaft 41 s is fixed to the input of the housing 40 of the epicyclic wheel 35 (b) ring gear 42, at the output there is an output coaxial shaft 43 with ring gear 44. A ring gear 45 is located on the front inner wall 4 of the second PM next to the ring gear 42, a ring gear 46 is located on the rear inner wall 5 next to the ring gear 44. Switch clutch 46 47 (A) mounted on gear crown 7 a primary output shaft 6 for selectively connecting the ring gear 9, drives a sun gear 17 (a), with a ring gear 22 drives carrier 19 (h). The shift clutch 48 (B) is located on the ring gear 30 of the front inner wall 2 for stopping the carrier 19 (h) with the ring gear 22 or the epicyclic wheel 20 with the ring gear 27, the off state (H) is provided by moving it to the wall 2. The switch clutch 49 (C ) is located on the ring gear 31 of the rear inner wall 3 to stop the epicyclic wheel 20 (b) ring gear 29 or the carrier 19 (h) ring gear 24, the off state (H) is provided by its movement to the wall 3. The shift clutch 50 (D) is installed on toothed ring de intermediate link 14 for selective connection with the gear rim 29 of the output coaxial shaft 28 of the epicyclic wheel 20 (b) or with the gear rim 24 of the output tubular shaft 23 of the carrier 19 (h) or with the gear rim 10 of the shaft 8, the neutral (N) state is ensured by the installation couplings between the crowns or its movement to the extreme right position. The coupling 51 (E) is located on the gear at the output of the intermediate link 14 for driving the sun gear 32 of the second PM when connecting to the gear ring 12 of the shaft 11 or for driving the carrier 34 when connecting to the gear ring 37 of the tubular input shaft 36 or the gear wheel 35 with the gear crown 42, a neutral (H) state is provided by installing the coupling between the ring gears or by moving it to the leftmost position. The shift clutch 52 (F) is located on the gear ring 45 of the front inner wall 4 of the second PM for stopping the carrier 34 (h) with the gear ring 37 or the epicyclic wheel 35 with the gear ring 42, the off state (H) is provided by its movement to the wall 4. The switch clutch 53 (G) is located on the ring gear 46 of the rear inner wall 5 for stopping the epicyclic wheel 35 (b) the ring gear 44 or the carrier 34 (h) the ring gear 39, the off state (H) is provided by its movement to the wall 5. Three-position switching clutch 54 (H) setting Lena on the gear ring 16 at the input of the secondary shaft 15 for selectively connecting with the ring gear 44 of the output coaxial shaft 43 of the epicyclic wheel 35 (b) or with the ring gear 39 of the output tubular shaft 38 of the carrier 34 (h) or with the ring gear 13 of the sun gear shaft 11 32, a neutral (H) state is ensured by the installation of the coupling between the crowns or its movement to the extreme right position.

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 control panel in question, we do not use integral (summing) modes.

1st gear PM: U _hb ^a = K + 1; 2nd gear PM: U _bh ^a = (K + 1) / K;

3rd gear PM: Direct U = 1,0;

4th gear PM: U _hb ^a = K / (K + 1); 5th gear PM: U _hb ^b = 1 / (K + 1);

1st reverse gear PM: U _ab ^h = -K; 2nd reverse gear PM: U _ba ^h = - (1 / K).

A minus sign indicates a change in the direction of rotation at the output compared to the input. Of the 5 forward gears, we do not use gears with the sun gear stopped: 2nd gear PM: U _bh ^a = (K + 1) / K; 4th gear PM: U _hb ^a = K / (K + 1). The following options remain:

When K ₁ = 3.0 we get: U _ah ^b ₁ = K ₁ + l = 4.0; lq 4.0 = 0.6;

U = 1.0; lq 1.0 = 0.0.

U _ha ^b ₁ = 1 / (K ₁ +1) = 1 / 4.0 = 0.25; lq 0.25 = -0.6.

U _ab ^h ₁ = -K ₁ = 3.0; lq 3.0 = 0.477;

U _ba ^h ₁ = - (1 / K ₁ ) = 1/3 = 0.333; lq 0.333 = -0.477.

When K ₂ = 1.5 we get: U _ah ^b ₂ = K ₂ + l = 2.5; lq 2.5 = 0.4;

U = 1.0; lq 1.0 = 0.0.

U _ha ^b ₂ = 1 / (K ₂ +1) = 1 / 2.5 = 0.4; lq 0.4 = -0.4.

U _ab ^h ₂ = -K ₂ = 1.5; lq 1.5 = 0.176;

U _ba ^h ₂ = - (l / K ₂ ) = 1 / 1.5 = 0.67; lq 0.67 = -0.176.

The device operates as follows.

First gear

In the beam diagram (Fig. 2), this mode is indicated by two consecutive gentle rays U _ah ^b ₁ and U _ah ^b _{2 to the} right upwards from t. 0 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 E - left (L); B and F - right (P), D and H - average (C), C and G - neutral (H), off. The upper part of the table shows the U _ah ^b state of the PM.

The epicyclic wheel 20 (b) of the first PM is stopped by a coupling 48 (B), which closes the gears 30 of the front inner wall 2 and 27 of the coaxial shaft 26 of the housing 25 of the epicyclic wheel 20. The couplings 48 (B) and 49 (C) partially overlap one another. Clutch 49 (C) can be in a neutral (H), off position or close the ring gears 31 of the rear inner wall 3 and 29 of the coaxial shaft 28 of the housing 25 of the epicyclic wheel 20 or the ring gear 24 of the carrier 19. The epicyclic wheel 35 (b) of the second PM can be stopped by a clutch 52 (F), which closes the gears 45 of the front inner wall 4 and 42 of the coaxial shaft 41 of the housing 40 of the epicyclic wheel 35. Clutches 52 (F) and 53 (G) also partially overlap one another.

The torque (Fig. 1) from the input shaft 6, the ring gear 7 by the coupling 47 (A) is transmitted by the shaft 8 to the sun gear 17 (a). The sun gear 17 (a) rotates the satellites 18, which, rolling around the epicyclic wheel 20 (b), rotate the carrier 19 (h) with a reduced frequency, but with increased torque. The tubular shaft 23, the ring gear 24, the coupling 50 (D) torque is supplied to the input gear ring of the intermediate link 14, then the output gear ring of the link 14, the coupling 51 (E) is transmitted to the ring gear 12 and the shaft 11 to the sun gear 32 (a ) of the second PM. The sun gear 32 (a) rotates the satellites 33, which, rolling around the epicyclic wheel 35 (b), rotate the carrier 34 (h) with a reduced frequency, but with increased torque. The tubular shaft 38, the ring gear 39, the coupling 54 (N) torque is supplied to the ring gear 16 and the secondary shaft 15.

When K ₁ = 3.0 and K ₂ = 1.5, the gear ratio of the 1st gear

U _1n = (K ₁ +1) (K ₂ +1) = 4.0 * 2.5 = 10.0; lq 10.0 = 1.0.

Second gear

In the beam diagram (Fig. 2), this mode is indicated by a shallow beam U _ab ^h _{1 of the} first PM from v. 0 to the right down and a ray of U _ab ^h _{2 to the} right up, then the dotted line to v. 2 on the upper horizontal.

We switch couplings B and F from the right state to the middle (C), D and H - from the middle to the left (L). The state of both PMs changed U _ab ^h = -K. Both PM work in reverse mode, forming a forward gear.

The carrier of the first PM was stopped by the coupling 48 (B), which closed the ring gear 30 of the front wall 2 and the ring gear 22 of the tubular shaft 21 of the carrier 19. The carrier of the second PM was stopped by the sleeve 52 (F), which closed the ring gear 45 of the front wall 4 and the ring gear 37 tubular output shaft 36 drove 34.

Torque (Fig. 1) is transmitted to the sun gear 17 (a) as in 1st forward gear. The sun gear 17 (a) rotates the satellites 18, which, rotating on the axes of the carrier 19 (h), rotate the epicyclic wheel 20 (b) in the opposite direction with a lower speed, but with increased torque. Next, a coaxial shaft 28, a gear ring 29, a coupling 50 (D) to the intermediate link 14, then as in 1st gear to the sun gear 32 of the second PM. The sun gear 32 (a) rotates the satellites 33, which, rotating on the axes of the carrier 34 (h), rotate the epicyclic wheel 35 (b) in the opposite direction with a lower speed, but with increased torque. With the coaxial shaft 43, the ring gear 44, the coupling 54 (H), torque is supplied to the ring gear 16 and the secondary shaft 15.

When K ₁ = 3.0 and K ₂ = 1.5, the gear ratio of 2nd gear

U _2n = (K1) (K ₂ ) = 3.0 * 1.5 = 4.5; lq 4.5 = 0.65.

Third gear

In the beam diagram (Fig. 2), this mode is indicated by two beams: a gentle beam U _ah ^b ₁ from t. 0 to the right upwards, then a vertical beam U ₂ = 1.0 to t. 3.

Compared with the 1st gear, we switch the clutches: E from the left position to the middle position (C), F from the right state to neutral (H), off, 1st PM works as in 1st gear, 2nd works in direct transmission.

Torque from the input shaft 6 and the ring gear 7 to the intermediate link 14 is supplied in the 1st gear, then the clutch 51 (E) is transmitted to the ring gear 37, the tubular shaft 36 and the carrier 34, then in the 1st gear.

With K ₁ = 3.0 and K ₂ = 1.5, the gear ratio of 3rd gear

U _3n = (K ₁ +1) = 4.0; lq 4.0 = 0.6.

Fourth gear

In the beam diagram (Fig. 2), this mode is indicated by two beams: from t. 0 the vertical beam U ₁ = 1,0, then the beam U _ah ^b _{2 to the} right upwards to t. 4.

In comparison with the 3rd gear, we switch the clutches: A from the left position to the middle position (C), B from the right position to the neutral position (N), switched off; E from middle to left (L); F from neutral to right (P) state; PM states have changed: 1st PM is in direct gear, 2nd PM is in 1st gear U _ah ^b ₂ .

Torque from the input shaft 6 and the ring gear 7 through the clutch 47 (A) is supplied to the ring gear 22, the input tubular shaft 21, then to the carrier 19 and as in 1st gear.

When K ₁ = 3.0 and K ₂ = 1.5, the gear ratio of 4th gear

U _4n = (K ₂ +1) = 2.5; lq 2.5 = 0.4.

Fifth gear

In the beam diagram (Fig. 2), similarly to the 2nd gear, this mode is indicated by a gentle beam U _ab ^h _{1 of the} first PM from t. 0 to the right down and to the beam U _ab ^h ₂ but to the left up, then the dotted line to t. 5 on the upper horizontal .

Compared with the 4th gear, we switch the clutches: A and D from middle to left (L) position, B from neutral to middle (C), E from left to right (P); F from right to neutral (H) off; G from neutral to secondary (C); N from middle to right (P) - both PM work in reverse modes.

The carriers of both PMs were stopped in 2nd gear, but in the 2nd PM the clutch G, which closed the ring gears 46 of the rear wall 5 and 39 of the output tubular shaft 38, drove 34.

The torque to the intermediate link 14 comes in 2nd gear, then the clutch 51 (E) on the ring gear 42 of the coaxial input shaft 41 (clutch 52 (F) in the far right, near the inner wall 4, off (H) state) the epicyclic wheel 35 rotates the satellites 33 on the axles of the carrier 34, they rotate the sun gear 32 in the opposite direction with respect to the PM input with an increased frequency, but with a reduced torque. Next, the shaft 11, the ring gear 13, the coupling 54 (N) torque is supplied to the ring gear 16 and the secondary shaft 15.

When K ₁ = 3.0 and K ₂ = 1.5, the gear ratio of the 5th gear

U _5n = (K ₁ ) (1 / K ₂ ) = 3.0 * (1 / 1.5) = 2.0; lq 2.0 = 0.3.

Sixth gear

In the beam diagram (Fig. 2), this mode is indicated by two beams: from t. 0 a gentle beam U _ah ^b _{1 to the} right up, then the beam U _ha ^b _{2 to the} left to the top to t. 6.

Compared to the 5th gear, we switch clutch B from the middle position to the right (P), clutch D from the left to the middle (C), clutch E from the right to the middle (C), the clutch F from the neutral position to the right (P), coupling G from medium to neutral (H), off position; there was a replacement of the PM states: 1st PM in the state of 1st and 3rd gears, 2nd PM in the state of U _ha ^b .

The torque from the input shaft 6 and the ring gear 7 to the clutch E is transmitted both in 1st and 3rd gears, then to the ring gear 37, the tubular shaft 36 and the carrier 34. The satellites 33 rotate relative to the stopped epicyclic wheel 35, rotate the sun gear 32, the shaft 11, from the ring gear 13 by the coupling N to the ring gear 16 and the secondary shaft 15.

When K ₁ = 3.0 and K ₂ = 1.5, the gear ratio of the 6th gear

U _6n = (K ₁ +1) [1 / (K ₂ +1)] = 4.0 * (1 / 2.5) = 1.6; lq 1.6 = 0.204.

Seventh gear - direct

On the beam diagram, this transmission is represented by two vertical rays from t. 0 to t. 7.

We switch the couplings: A from the left position to the middle (C), couplings B and F from the right to neutral (H), off; coupling N from the right to the middle position (C). Both PMs are in direct transmission by carrier.

Torque (Fig. 1) from the input shaft 6 to the intermediate link 14 is transmitted as in 4th gear, then as in 3rd gear.

When K ₁ = 3.0 and K ₂ = 1.5, the gear ratio of the 7th gear

U _7p = 1.0; lq 1.0 = 0.0.

Eighth gear

In the beam diagram (Fig. 2), this mode is indicated by two beams: a gentle beam U _ha ^b ₁ from point 0 to the left up, then the beam U _ah ^b _{2 to the} right up to point 8.

We switch couplings B and F from neutral to right (P), couplings D and E from middle to right (P) and left (L) positions.

Epicyclic wheels 20 (b) of the first PM and 35 of the second PM are stopped as in 1st gear. Torque (Fig. 1) from the input shaft 6, the ring gear 7 by the clutch A is transmitted to the ring gear 22, the tubular shaft 21 and the carrier 19 as in 7th gear. Satellites 18 on the axes of carrier 19 rotate the sun gear 17, then from the ring gear 10 by the clutch D to the intermediate link 14, then as in the 1st and 4th gears.

When K ₁ = 3.0 and K ₂ = 1.5, the gear ratio of the 8th gear

U _8n = [1 / (K ₁ +1)] (K ₂ +1) = (1 / 4.0) 2.5 = 0.625; lq 0.625 = -0.204.

Ninth gear

On the ray diagram, this transmission is represented by two rays: from t. 0 ray U _ba ^h _{1 to the} left down, then U _ba ^h _{1 to the} right up, then the dotted line to t. 9.

We switch the couplings: A from the middle to the right (P) position, B from the right position to neutral (H), off; C from neutral to middle (C), F from right to middle (C) and clutch H from mid to left (L). The first PM in the state U _ba ^h ₁ , the second PM in the state U _ab ^h ₂ .

Torque from the input shaft 6, ring gear 7 by clutch A is transmitted to ring gear 27, coaxial shaft 26, housing 25, epicyclic wheel 20, which rotates the satellites 18 on the axles of carrier 19 and transmits rotation in the opposite direction to the sun gear 17, shaft 8 , gear ring 10, clutch D on the intermediate link 14, then as in 2nd gear.

When K ₁ = 3.0 and K ₂ = 1.5, the gear ratio of the 9th gear

U _9n = {1 / K ₁ ) K ₂ = (1 / 3.0) * 1.5 = 0.5; lq 0.5 = -0.3.

Tenth gear

On the beam diagram, this transmission is represented by two rays: from t. 0 a vertical beam, then U _ha ^b _{2 from the} left up to t. 10.

We switch couplings: A and D from the right position to the middle (C), C from the middle to neutral (H), the off position; E from the left to the middle (C) position, F from the middle position to the right (P) and the coupling N from the left position to the right (P). The first PM in the direct transmission state, the second PM in the state U _ha ^b ₂ .

Torque (Fig. 1) from the input shaft 6 to the intermediate link 14 is transmitted both in 4th and 7th gears, then as in 6th gear.

When K ₁ = 3.0 and K ₂ = 1.5, the gear ratio of the 10th gear

U _10n = [1 / (K ₂ +1)] = 1 / 2.5 = 0.4; lq 0.4 = -0.4.

Eleventh gear

In the beam diagram (Fig. 2), this mode is indicated by two beams: a gentle beam U _ha ^b ₁ from t. 0 to the left up, then a vertical beam U ₂ = 1,0 to t. 11.

We switch the clutch: B from neutral to right (P), D from middle to right (P), F from right to neutral (H), off; N from the right in the middle (C) position.

The epicyclic wheels 20 (b) of the first PM are stopped in 1st, 3rd, 6th and 8th gears. Torque (Fig. 1) from the input shaft 6 to the intermediate link 14 is transmitted in 8th gear, then in 7th gear.

When K ₁ = 3.0 and K ₂ = 1.5, the gear ratio of the 11th gear

U _11n = 1 / (K ₁ +1) = 1 / 4.0 = 0.25; lq 0.25 = -0.6.

Twelfth gear

On the ray diagram this transmission is represented by two beams: from t. 0 a gentle beam U _ba ^h ₁ left down, then U _ba ^h ₂ left up, then a dashed line to t. 12.

We switch the couplings: A and H from the middle to the right (P) position, B from the right position to neutral (H), off; C and G from neutral to middle (C), E from middle to right (P). Both PM in the state of U _ba ^h .

Torque (Fig. 1) from the input shaft 6 to the intermediate link 14 is transmitted in 9th gear, then in 5th gear.

When K ₁ = 3.0 and K ₂ = 1.5, the gear ratio of the 12th gear

U _12n = (l / K ₁ ) (1 / K ₂ ) = (1 / 3.0) * (1 / 1.5) = 0.222; lq 0.222 = -0.65.

Thirteenth gear

In the beam diagram (Fig. 2), this mode is indicated by two beams: a gentle beam U _ha ^b ₁ from point 0 to the left up, then the beam U _ha ^b ₂ to point 13.

We switch the couplings: A and E from the right to the middle (C) position, B and F from neutral to right (P), C and G from middle to neutral (H), off.

Epicyclic wheels 20 (b) of the first PM and 35 of the second PM are stopped in 1st, 6th and 8th gears.

Torque (Fig. 1) from the input shaft 6 to the intermediate link 14 is transmitted as in the 8th and 11th gears, then as in the 6th and 10th gears.

When K ₁ = 3.0 and K ₂ = 1.5, the gear ratio of the 13th gear

U _13n = [1 / (K + 1)] [1 / (K ₂ +0] = (1 / 4.0) (1 / 2.5) = 0.1; lq 0.25 = -1.0 .

First gear reverse 1R

In the beam diagram (Fig. 2), this mode is indicated by two rays:

from t. 0 a gentle beam U _ab ^h _{1 to the} right down, then the beam U _ab ^h ₂ also to the right down to t. 1R.

Below this point, the states of the switching clutches are shown: A, D, E and G - left (L), B and H - average (C), C and F - neutral (H), off. At the bottom of the table are shown U _ab ^h ₁ and U _ab ^h ₂ states of the PM.

Drove 19 of the first PM was stopped by clutch B, which closed the gear rims 30 of the front inner wall 2 and 27 of the tubular input shaft 21 of drove 19.

Torque (Fig. 1) from the input shaft 6 to the sun gear 17 is transmitted in the 1st, 3rd and 6th forward gears. The sun gear 17 (a) rotates the satellites 18, which, rotating on the axes of the carrier 19, rotate the epicyclic wheel 20 (b), the housing 25, the coaxial shaft 28 in the opposite direction to the rotation of the sun gear with a reduced frequency, but with increased torque. From the ring gear 29 by the clutch D, the torque is supplied to the intermediate link 14, then as in the 1st, 4th and 8th forward gears.

With K ₁ = 3.0 and K ₂ = 1.5, the gear ratio of the 1st reverse gear is 1R

U _1R = (K ₁ ) (K ₂ +1) = 3.0 * 2.5 = 7.5; lq 7.5 = 0.875.

Second gear reverse 2R

In the beam diagram (Fig. 2), this mode is indicated by two beams: from t. 0 a gentle beam U _ah ^b _{1 to the} right up, then the beam U _ab ^h _{2 to the} right, then the dotted line to t. 2R.

We switch the clutch: B from middle to right (P), D from left to middle (C), F from neutral to right (P), G from left to neutral (H), off; N from middle to left (L). At the bottom of the table are shown U _ah ^b ₁ and U _ab ^h ₂ state of the PM.

Torque (Fig. 1) from the input shaft 6 to the intermediate link 14 is transmitted as in the 1st, 3rd and 6th forward gears, then as in the 2nd forward gear.

When K ₁ = 3.0 and K ₂ = 1.5, the gear ratio of the 2nd reverse gear 2R

U _2R = (K ₁ +1) (K ₂ ) = 4.0 * 1.5 = 6.0; lq 6.0 = 0.78.

Third gear reverse 3R

In the beam diagram (Fig. 2), this mode is indicated by two beams: from t. 0 a gentle beam U _ab ^h _{1 to the} right down, then a vertical beam U ₂ = 1.0 to t. 3R.

Compared with the 1st reverse gear, we switch the clutches: E from left to middle (C), G from left to neutral (H), off. The bottom part of the table shows U _ab ^h ₁ and U = 1,0 state of the PM.

Torque (Fig. 1) from the input shaft 6 to the intermediate link 14 is transmitted as in the 1st reverse gear, then in the 3rd, 7th and 11th forward gears.

When K ₁ = 3.0 and K ₂ = 1.5, the gear ratio of the 3rd reverse gear 3R

U _3R = K ₁ = 3.0; lq 3.0 = 0.477.

Fourth Reverse 4R

In the beam diagram (Fig. 2), this mode is indicated by two beams: from t. 0 a gentle beam U _ah ^b _{1 to the} right up, then the beam U _ba ^h _{2 to the} left down, then the dashed line to t.

Compared with the 2nd reverse gear, we switch the clutches E and H from the left position to the right (P), the clutch F from the right to the neutral (H), off position; coupling G from neutral to medium (C),

Torque from the input shaft 6 to the intermediate link 14 is transmitted as in the 1st, 3rd and 6th gears, then by the clutch E to the ring gear 42, the coaxial shaft 41, the housing 40 and the epicyclic wheel 35. The satellites 33 rotate on the axles drove 34, rotate the sun gear 32, the shaft 11, from the ring gear 13 by the coupling N to the ring gear 16 and the secondary shaft 15.

With K ₁ = 3.0 and K ₂ = 1.5, the gear ratio of the 4th reverse gear is 4R

U _4R = (K ₁ +1) (1 / K ₂ ) = 4.0 * (1 / 1.5) = 2.67; lq 2.67 = 0.426.

5R reverse gear 5R

In the beam diagram (Fig. 2), this mode is indicated by two rays: from t. 0 the vertical beam U ₁ = 1.0 up, then the beam U _ab ^h _{2 to the} right down, then the dotted line to t. 5R.

In comparison with the 4th reverse gear, we switch the clutches: A from the left position to the middle (C), B from the right to the neutral (H), off position; E and H from right to left (L) position.

The torque from the input shaft 6 to the intermediate link 14 is transmitted as in 4th, 7th and 10th forward gears, then as in 2nd reverse gear.

With K ₁ = 3.0 and K ₂ = 1.5, the gear ratio of the 5th reverse gear 5R

U _5R = K ₂ = 1.5; lq 1.5 = 0.176.

6R reverse gear 6R

In the beam diagram (Fig. 2), this mode is indicated by two beams: from t. 0 a gentle beam U _ab ^h _{1 to the} right down, then the beam U _ha ^b ₂ left down to t. 6R.

We switch couplings: AD to the states of the 1st and 3rd reverse gears; compared with the previous transmission: E from left to middle (C), G from middle to left (L), H from left to right (P). At the bottom of the table are shown U _ab ^h ₁ and U _ha ^b ₂ state of the PM.

Torque (Fig. 1) from the input shaft 6 to the intermediate link 14 is transmitted both in the 1st and 3rd reverse gears, then as in the 6th, 10th and 13th forward gears.

With K ₁ = 3.0 and K ₂ = 1.5, the gear ratio of the 6th reverse gear is 6R

U _6R = (K) * 1 / (K ₂ +1) = 3.0 * (1 / 2.5) = 1.2; lq 1.2 = 0.079.

Seventh gear reverse 7R

In the beam diagram (Fig. 2), this mode is indicated by two beams: from t. 0 a gentle beam U _ba ^h _{1 to the} left down, then the beam U _ah ^b _{2 to the} right down to t. 7R.

Below this point are shown the states of the clutch: EH correspond to the positions of the 1st reverse gear; compared with the previous transmission: A and D from left to right (P), B - from medium to neutral (H), off; C from neutral to secondary (C). At the bottom of the table are shown U _ba ^h ₁ and U _ah ^b ₂ state PM.

Drove 19 of the first PM was stopped by clutch C, which closed the ring gears 31 of the rear inner wall 3 and 28 of the tubular output shaft 23 of drove 19.

The torque (Fig. 1) from the input shaft 6 and the ring gear 7 to the epicyclic wheel 20 (b) is transmitted by the clutch A, the ring gear 27, the coaxial input shaft 26 and the housing 25. The epicyclic wheel 20 (b) rotates the satellites 18, which, rotating on the axles of the carrier 19, rotate the sun gear 17 (a), then the shaft 8, the ring gear 10 and the clutch D on the intermediate link 14, then as in the 1st reverse gear.

With K ₁ = 3.0 and K ₂ = 1.5, the gear ratio of the 7th reverse gear is 7R

U _7R = (1 / K ₁ ) (K ₂ +1) = (1 / 3.0) * 2.5 = 0.833; lq 0.833 = -0.079.

8R reverse gear 8R

In the beam diagram (Fig. 2), this mode is indicated by two beams: from t. 0 the vertical beam U ₁ = 1.0 up, then the beam U _ba ^h ₂ left down, then the dashed line to t. 8R.

Compared with the 5th reverse gear, we switch the clutches E and H from the left to the right (P) position.

The torque from the input shaft 6 to the intermediate link 14 is transmitted as in 5th reverse gear, then as in 4th reverse gear.

With K ₁ = 3.0 and K ₂ = 1.5, the gear ratio of the 8th reverse gear is 8R

U _8R = 1 / K ₂ = 1 / 1.5 = 0.667; lq 0.667 = -0.176.

9R reverse gear 9R

In the beam diagram (Fig. 2), this mode is indicated by two beams: from t. 0 a gentle beam U _ha ^b _{1 to the} left up, then the beam U _ab ^h _{2 to the} right down, then the dotted line to t. 9R.

Compared with the 5th reverse gear, we switch the clutch D from the middle position to the right (P).

The torque from the input shaft 6 to the intermediate link 14 is transmitted as in the 8th, 11th and 13th forward gears, then as in the 2nd and 5th reverse gears.

With K ₁ = 3.0 and K ₂ = 1.5, the gear ratio of the 9th reverse gear 9R

U _9R = 1 / (K ₁ +1) K ₂ = (1/4) 1.5 = 0.375; lq 0.375 = -0.426.

10R reverse gear 10R

In the beam diagram (Fig. 2), this mode is indicated by two beams: from t. 0 a gentle beam U _ba ^h ₁ left down, then a vertical beam U ₂ = 1,0 down to t. 10R.

Compared with the 7th reverse gear, we switch from the left position of the clutch: E - to the middle (C), G - to neutral (H), off position. At the bottom of the table, U _ba ^h ₁ and U ₂ = 1.0 state of the PM are shown.

The torque from the input shaft 6 to the intermediate link 14 is transmitted as in the 7th reverse gear, then as in the 3rd reverse gear.

When K ₁ = 3.0 and K ₂ = 1.5, the gear ratio of the 10th reverse gear 10R

U _10R = 1 / K ₁ = 1 / 3.0 = 0.333; lq 0.333 = -0.477.

11th reverse gear 11R

In the beam diagram (Fig. 2), this mode is indicated by two beams: from t. 0 a gentle beam U _ha ^b _{1 to the} left up, then the beam U _ba ^h _{2 to the} left down, then the dotted line to t. 11R.

Compared with the 9th reverse gear, we switch the clutches E and H from the left to the right (P) position.

Torque from the input shaft 6 to the intermediate link 14 is transmitted as in the 9th reverse gear, then as in the 4th and 8th reverse gears.

With K ₁ = 3.0 and K ₂ = 1.5, the gear ratio of the 11th reverse gear is 11R

U _11R = [1 / (K ₁ +1)] (1 / K ₂ ) = (1 / 4.0) (1 / 1.5) = 0.167; lq 0.167 = -0.78.

12th reverse gear 12R

In the beam diagram (Fig. 2), this mode is indicated by two beams: from t. 0 a gentle beam U _ba ^h ₁ left down, then the beam U _ha ^b ₂ left down to t. 12R.

Compared with the 10th reverse gear, we switch clutch G from neutral to left (L) position, clutch H from middle to right (P). At the bottom of the table are shown U _ba ^h ₁ and U _ha ^b ₂ state PM.

Torque from the input shaft 6 to the intermediate link 14 is transmitted as in the 7th and 10th reverse gears, then as in the 6th reverse gear.

With K ₁ = 3.0 and K ₂ = 1.5, the gear ratio of the 12th reverse gear is 12R

C _12R = (1 / K ₁ ) [1 / (K ₂ +1)] = (1 / 3.0) (1 / 2.5) = 0.133; lq 0.133 = - 0.875.

The control panel range was D = U ₁ / U ₁₃ = 10.0 / 0.1 = 100.

Got a close to optimal distribution of gear ratios over the range.

Changing K will change the kinematic characteristics of the control panel.

Got a compact transmission unit of low metal consumption, which creates better conditions for the layout of the engine and transmission. Enhanced vehicle performance by increasing the range and number of gears.

Designations:

1 - housing of the control panel (planetary gearbox);

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

3 - the inner back wall of the first PM;

4 - the inner front wall of the second PM;

5 - the inner back wall of the second PM;

6 - a primary shaft;

7 - a gear ring mounted on the input shaft 6;

8 - the drive shaft of the sun gear of the first PM;

9 - input gear ring of the drive shaft of the sun gear of the first PM;

10 - the output gear ring of the drive shaft of the sun gear of the first PM;

11 - the drive shaft of the sun gear of the second PM;

12 - input gear ring of the drive shaft of the sun gear of the second PM;

13 - the output gear ring of the drive shaft of the sun gear of the second PM;

14 - an intermediate link equipped with gear rims;

15 - a secondary shaft;

16 - a gear ring mounted on the secondary shaft 15;

17 (a) - the sun gear of the first PM;

18 - satellites on the axles drove 19;

19 (h) - drove the first PM;

20 (b) is the epicyclic wheel of the first PM;

21 - tubular input shaft of carrier 19 (h);

22 - the ring gear of the tubular shaft 21 at the inlet of the carrier 19 (h);

23 - tubular output shaft of carrier 19 (h);

24 - the ring gear of the tubular shaft 23 at the outlet of the carrier 19 (h);

25 - the body of the epicyclic wheel 20;

26 - input coaxial shaft of the housing 25 of the epicyclic wheel 20;

27 - the gear rim of the input coaxial shaft 26;

28 - output coaxial shaft of the housing 25 of the epicyclic wheel 20;

29 - the gear rim of the output coaxial shaft 28;

30 - the gear ring of the front inner wall 2;

31 - the gear rim of the rear inner wall 3;

32 (a) - the sun gear of the second PM;

33 - satellites on the axles drove 34;

34 (h) - drove the second PM;

35 (b) is the epicyclic wheel of the second PM;

36 - tubular input shaft of carrier 34 (h);

37 - the ring gear of the tubular shaft 36 at the inlet of the carrier 34 (h);

38 - tubular output shaft of carrier 34 (h);

39 - the gear rim of the tubular shaft 38 at the output of the carrier 34 (h);

40 - the body of the epicyclic wheel 35;

41 - input coaxial shaft of the housing 40 of the epicyclic wheel 35;

42 - the gear rim of the input coaxial shaft 41;

43 - output coaxial shaft of the housing 40 of the epicyclic wheel 35;

44 - the gear rim of the output coaxial shaft 43;

45 - the gear ring of the front inner wall 4 of the second PM;

46 - the gear ring of the rear inner wall 5;

47 (A) - switching clutch on the ring gear 7 at the output of the input shaft 6;

48 (B) - coupling stop carrier 19 or epicyclic wheels 20 of the first PM on the gear ring 30 of the front inner wall 2;

49 (C) - stopping sleeve of the epicyclic wheel 20 or drove 19 of the first PM on the ring gear 31 of the rear inner wall 3;

50 (D) - switching clutch on the gear ring of the input of the intermediate link 14;

51 (E) - switching clutch on the gear ring of the output of the intermediate link 14;

52 (F) - coupling stop carrier 34 or epicyclic wheels 35 of the second PM on the gear ring 45 of the front inner wall 4;

53 (G) - the stop clutch of the epicyclic wheel 35 or drove 34 of the second PM on the ring gear 46 of the rear inner wall 5;

54 (N) - three-position switching clutch on the ring gear 16 of the secondary shaft 15.

Claims (1)

A planetary gearbox comprising a housing with primary and secondary shafts installed in it, two simple three-link planetary gears, each consisting of a carrier with satellites engaged with a sun gear and an epicyclic wheel, characterized in that in the bearings of the gearbox housing with internal walls between the primary and secondary shafts equipped with gear rims with switching clutches, shafts are installed coaxially: drive solar gears of planetary gears with an intermediate gear located between them link with ring gears and two switching clutches; the input and output tubular shafts of the carrier with the gear rims are freely mounted on the shafts of the drive gear of the sun gear with gear rims on the ends; the coaxial shafts of the epicyclic wheel body with gear rims are located on the tubular shafts; on the walls of the housings of planetary gears next to the gear rims of the input and output shafts, gear rims with stop couplings of the carrier or epicyclic wheel are fixed.

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